DK177019B1 - A pressure relief valve - Google Patents
A pressure relief valve Download PDFInfo
- Publication number
- DK177019B1 DK177019B1 DKPA200701396A DKPA200701396A DK177019B1 DK 177019 B1 DK177019 B1 DK 177019B1 DK PA200701396 A DKPA200701396 A DK PA200701396A DK PA200701396 A DKPA200701396 A DK PA200701396A DK 177019 B1 DK177019 B1 DK 177019B1
- Authority
- DK
- Denmark
- Prior art keywords
- valve
- flow tube
- width
- pressure relief
- relief valve
- Prior art date
Links
- 229910001220 stainless steel Inorganic materials 0.000 claims description 2
- 239000010935 stainless steel Substances 0.000 claims description 2
- 239000007789 gas Substances 0.000 description 14
- 238000004519 manufacturing process Methods 0.000 description 6
- 238000012423 maintenance Methods 0.000 description 5
- 230000010355 oscillation Effects 0.000 description 3
- RNFJDJUURJAICM-UHFFFAOYSA-N 2,2,4,4,6,6-hexaphenoxy-1,3,5-triaza-2$l^{5},4$l^{5},6$l^{5}-triphosphacyclohexa-1,3,5-triene Chemical compound N=1P(OC=2C=CC=CC=2)(OC=2C=CC=CC=2)=NP(OC=2C=CC=CC=2)(OC=2C=CC=CC=2)=NP=1(OC=1C=CC=CC=1)OC1=CC=CC=C1 RNFJDJUURJAICM-UHFFFAOYSA-N 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 239000003063 flame retardant Substances 0.000 description 2
- 239000000126 substance Substances 0.000 description 2
- 238000012360 testing method Methods 0.000 description 2
- 239000010426 asphalt Substances 0.000 description 1
- 230000003542 behavioural effect Effects 0.000 description 1
- 230000033228 biological regulation Effects 0.000 description 1
- 150000001720 carbohydrates Chemical class 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 235000013399 edible fruits Nutrition 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000008520 organization Effects 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 238000013519 translation Methods 0.000 description 1
Classifications
-
- 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
- F16K17/12—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side weight-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
- F16K17/0433—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 vibration preventing means
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Safety Valves (AREA)
- Lift Valve (AREA)
Abstract
Trykudligningsventil med et flowrør, hvor flowrørets højde er lig med eller større end flowrørets tredje bredde.Pressure equalization valve with a flow pipe, where the height of the flow pipe is equal to or greater than the third width of the flow pipe.
Description
DK 177019 B1 iDK 177019 B1 i
Trykudligningsventil Opfindelsens områdeField of Invention Pressure Relief Valve
Den foreliggende opfindelse angår en trykudligningsventil til trykudjævning 5 mellem et lukket rum og den omgivende atmosfære. Opfindelsen angår mere specifikt området inden for ventiler til højhastighedstrykudligning.The present invention relates to a pressure equalization valve for pressure equalization 5 between a closed space and the ambient atmosphere. More specifically, the invention relates to the field of high speed pressure relief valves.
Sådanne trykudligningsventiler anvendes især som trykudligningsorgan i opstillinger, hvor fx en last eller et stationært varelager udsender gasser med en 10 variabel hastighed. En sådan opstilling kan omfatte tanke til brændbare carbohydrater, især under påfyldning af sådanne tanke, kemiske laster, laster med asfalt eller faste stoffer, såsom frugt, der med tiden udsender gasser ved lagring.Such pressure relief valves are particularly used as pressure relief means in arrangements where, for example, a cargo or stationary warehouse emits gases at a variable rate. Such an arrangement may include flammable carbohydrate tanks, especially during filling such tanks, chemical loads, asphalt loads or solids, such as fruits which, over time, emit gases upon storage.
15 Ventiler af denne type kombineres sædvanligvis med vakuumventiler i tryk- vakuumhøjhastighedsventiler. Sådanne ventilers ydeevne er genstand for krav og internationale bestemmelser der fx er angivet i IMO MSC/Circ 677 fra den15 Valves of this type are usually combined with vacuum valves in pressure vacuum high speed valves. The performance of such valves is subject to requirements and international regulations specified in, for example, IMO MSC / Circ 677 from the
Internationale Maritime Organisation og Europæisk Standard EN 12874. ''j 20International Maritime Organization and European Standard EN 12874. '' j 20
Opfindelsens baggrundBACKGROUND OF THE INVENTION
Et almindeligt problem i forbindelse med trykudligningsventiler som anvendes i opstillinger hvor gas udsendes fra en substans der er begrænset i et lukket rum 25 med en konstant eller variabel hastighed, er et fænomen kaldet hamring eller oscillation.A common problem with pressure relief valves used in arrangements where gas is emitted from a substance confined in a closed space 25 at a constant or variable rate is a phenomenon called hammering or oscillation.
Trykudligningsventiler er udformet til at åbne ved et bestemt tryk der kan opbygges i det lukkede rum, og til at lukke når trykket vender tilbage til et 30 bestemt lavere tryk. I sådanne systemer har ventilen ofte tendens til at åbne og lukke meget hurtigt - hamring. Hamring/osciflation opstår på grund af en ubalance forårsaget af et tryktab i ventilen og rørsystemet nedstrøms i forhold til ventilen, således at ventilen under visse driftsbetingelser bevæger sig mellem sine ekstreme positioner (åben/lukket) ved en frekvens væsentligt over 0,5 Hz. Denne 35 bevægelse forårsager hårde stød mellem ventilelementet og ventilsædet (i lukket DK 177019 B1 2 position) og mellem ventilelementet og ventiltoppen (i åben position), hvilket med tiden vi! ødelægge de involverede dele. Hamring er således særdeles uønsket fordi dele af ventilerne vil blive udsat for tiltagende slitage, hvilket medfører et behov for kontinuerlig vedligeholdelse og/eifer udskiftning af ventiler eller ventildele.Pressure relief valves are designed to open at a specific pressure that can build up in the closed space and to close when the pressure returns to a certain lower pressure. In such systems, the valve often tends to open and close very quickly - hammering. Hammering / osciflation occurs due to an imbalance caused by a pressure loss in the valve and the pipe system downstream of the valve, so that the valve, under certain operating conditions, moves between its extreme positions (open / closed) at a frequency substantially above 0.5 Hz. This movement causes severe shocks between the valve element and the valve seat (in closed position DK 177019 B1 2) and between the valve element and the valve top (in the open position), which over time we! destroy the parts involved. Hammering is thus particularly undesirable because parts of the valves will be subject to increasing wear, which results in a need for continuous maintenance and / or replacement of valves or valve parts.
5 Hamring bevirker også at gasudstrømningsfrekvensen fra ventilen mellem ventilsædet og ventilelementet falder, hvorved en ønsket flammehæmmende egenskab ved sådanne ventiler reduceres eller elimineres.Hammering also causes the gas flow rate from the valve between the valve seat and the valve element to decrease, thereby reducing or eliminating a desired flame retardant property of such valves.
De ovennævnte bestemmelser kræver endvidere at hamringsfænomenet skal 10 elimineres eller reduceres for at bevare ventilernes ovennævnte flammehæmmende karakteristika.The above provisions further require that the hammering phenomenon must be eliminated or reduced in order to preserve the aforementioned flame retardant characteristics of the valves.
Trykudligningsventiler er kendte inden for teknikken. Et eksempel pi en sådan ventil er vist i WO 02/095275 Al. Denne ventil har magnetiske organer til sikring 15 af et bestemt åbningstryk for ventilen og en løfteplade til at hjælpe med at løfte ventilelementet. Da løftepladens område skal være større end den udstrømningsåbning der er defineret ved ventilsædet for at sikre flowdynamik, har denne ventils ventilhus en kompliceret geometrisk struktur. På grund af flowdynamikken rundt om løftepladen er hamring kun begrænset men ikke 20 fuldkommen reduceret. Denne ventils udformning er endvidere kompleks, hvilket medfører høje produktions- og vedligeholdelsesomkostninger og besværliggør nem vedligeholdelse.Pressure relief valves are known in the art. An example of such a valve is shown in WO 02/095275 A1. This valve has magnetic means for securing a specific opening pressure for the valve and a lifting plate to assist in lifting the valve member. Since the area of the lifting plate must be larger than the outflow opening defined by the valve seat to ensure flow dynamics, this valve's valve body has a complicated geometric structure. Due to the flow dynamics around the lifting plate, hammering is only limited but not fully reduced. Furthermore, the design of this valve is complex, which results in high production and maintenance costs and makes it difficult to maintain.
Den type ventilers geometri giver endvidere problemer med hensyn til 25 mellemrummet mellem løftepladen og ventilhusets væg. Der er et begrænset mellemrum mellem løftepladen og ventilhusets væg, hvilket gør denne type ventiler uegnede til klæbrige, krystalliserende og nedfrosne lasttyper. I den kendte teknik kompenseres der delvist for dette ved hjælp af ventilhusets klokkeform som til gengæld forårsager problemer med flowdynamikken.Furthermore, the geometry of the type of valve presents problems with respect to the gap between the lift plate and the wall of the valve body. There is a limited gap between the lift plate and the valve body wall, making these types of valves unsuitable for sticky, crystallizing and frozen load types. In the prior art this is partially compensated for by the bell shape of the valve body which in turn causes problems with flow dynamics.
3030
En forbedret trykudligningsventil vil derfor være fordelagtig, især en mere effektiv og/eller pålidelig trykudligningsventil.An improved pressure relief valve will therefore be advantageous, especially a more efficient and / or reliable pressure relief valve.
DK 177019 B1 3DK 177019 B1 3
Formål med opfindelsenObjects of the Invention
Det er et formål med opfindelsen at tilvejebringe en trykudligningsventi! til trykudjævning mellem et lukket rum og den omgivende atmosfære, hvorved hamrings-/oscillationskarakteristika elimineres.It is an object of the invention to provide a pressure relief valve! for pressure equalization between an enclosed space and the ambient atmosphere, thereby eliminating hammering / oscillation characteristics.
55
Det er et yderligere formål med den foreliggende opfindelse at tilvejebringe en trykudligningsventil med forlænget levetid og reduceret vedligeholdelsestid og reducerede vedligeholdelsesomkostninger.It is a further object of the present invention to provide an extended life pressure relief valve and reduced maintenance time and reduced maintenance costs.
10 Det er et yderligere formål med den foreliggende opfindelse at tilvejebringe en trykudligningsventil med en simplificeret konstruktion som er nem og omkostningseffektiv at fremstille, vedligeholde og reparere,It is a further object of the present invention to provide a pressure relief valve of a simplified design which is easy and cost effective to manufacture, maintain and repair.
Det er et yderligere formål med den foreliggende opfindelse at tilvejebringe et 15 alternativ til trykudligningsventiler ifølge den kendte teknik til trykudjævning mellem et lukket rum og den omgivende atmosfære.It is a further object of the present invention to provide an alternative to pressure equalization valves of the prior art for pressure equalization between a closed space and the ambient atmosphere.
Det kan især betragtes som et formål med den foreliggende opfindelse at tilvejebringe en trykudligningsventil der løser de ovennævnte problemer inden for 20 den kendte teknik.In particular, it can be considered an object of the present invention to provide a pressure relief valve that solves the above-mentioned problems in the prior art.
Kort beskrivelse af opfindelseoBrief Description of the Invention
Det er hensigten at det ovenfor beskrevne formål og flere andre formål skal opnås 25 i et første aspekt af opfindelsen ved at tilvejebringe en trykudligningsventil der omfatter ♦ et langstrakt ventilhus med o en indløbsende der kan forbindes med et lukket rum, o en udløbsende der er anbragt over for indløbsenden i huset, 30 o en langsgående midterakse og o en i det væsentlige ensartet første indvendig bredde der er vinkelret på midteraksen i et tværsnit langs midteraksen fra indløbsenden til udløbsenden, DK 177019 B1 4 • et ventilsæde der er anbragt ved udløbsenden, og som har en anden indvendig bredde der er vinkelret på midteraksen i tværsnit langs midteraksen, • et ventilelement der er anbragt til at samvirke med ventilsædet og er 5 anbragt til translationsbevægelse i en retning langs aksen for at tilvejebringe åbning og lukning af ventilen, • organ til tilvejebringelse af en modstandsevne mod åbning af ventilen, • et flowrør der er anbragt mellem indløbsenden og udløbsenden, og som har en tredje udvendig bredde der er vinkelret på midteraksen i et 10 tværsnit langs midteraksen, og en højde der er defineret mellem en første ende som vender mod indløbsenden, og en anden ende der vender mod udløbsenden; og • en forbindelse mellem ventilelementet og flowrøret, hvorved flowrøret og elementet er anbragt til samtidig translationsbevægelse langs aksen 15 hvor flowrørets højde er lig med eller større end flowrørets tredje bredde.It is intended that the above-described object and several other objects be achieved in a first aspect of the invention by providing a pressure equalizing valve comprising an elongated valve housing having an inlet end which can be connected to a closed space, an outlet end disposed therein. opposite the inlet end of the housing, 30 o a longitudinal center axis and o a substantially uniform first interior width perpendicular to the center axis in a cross section along the center axis from the inlet end to the outlet end, a valve seat disposed at the outlet end, having a second internal width perpendicular to the central axis in cross-section along the central axis; a valve member arranged to cooperate with the valve seat and arranged for translational movement in a direction along the axis to provide opening and closing of the valve; providing a resistance to opening the valve, • a flow tube disposed between the the outlet end and outlet end having a third outside width perpendicular to the center axis of a cross-section along the center axis, and a height defined between a first end facing the inlet end and a second end facing the outlet end; and • a connection between the valve element and the flow tube, whereby the flow tube and the element are arranged for simultaneous translational movement along the axis 15 where the height of the flow tube is equal to or greater than the third width of the flow tube.
Formålene med opfindelsen opnås yderligere med udførselsformer beskrevet i de forskellige afhængige krav.The objects of the invention are further achieved with embodiments described in the various dependent claims.
20 Kort beskrivelse af tegningen20 Brief Description of the Drawing
Trykudligningsventilen ifølge opfindelsen vil nu blive beskrevet mere detaljeret under henvisning til de ledsagende figurer. Figurerne viser måder til implementering af den foreliggende opfindelse og skal ikke fortolkes som værende 25 begrænsende for andre mulige udførelsesformer der ligger inden for omfanget af det vedhæftede sæt krav, • Fig. 1 viser i en delvis snitgengivelse en tryk-vakuumhøjhastighedsventil med en trykudligningsventil ifølge en udførelsesform af opfindelsen.The pressure relief valve according to the invention will now be described in more detail with reference to the accompanying figures. The figures show ways of implementing the present invention and are not to be construed as limiting other possible embodiments within the scope of the attached set of claims. 1 shows a partial sectional view of a pressure vacuum high speed valve with a pressure equalizing valve according to an embodiment of the invention.
30 • Fig. 2 viser i en snitgengivelse detaljer af en trykudligningsventil ifølge en udførelsesform af opfindelsen.FIG. 2 is a sectional view showing details of a pressure relief valve according to an embodiment of the invention.
• Fig. 3 viser et system der omfatter et lukket rum i form af en tank, og 35 viser forskellige anbringelser af en trykudligningsventil; og DK 177019 B1 5 • Fig. 4 viser adfærdskarakteristika for en trykudligningsventil ifølge en udførelsesform af opfindelsen i en testundersøgelse.FIG. 3 shows a system comprising a closed space in the form of a tank, and 35 shows various applications of a pressure relief valve; and DK 177019 B1 5. 4 shows the behavioral characteristics of a pressure relief valve according to one embodiment of the invention in a test study.
5 Udførelsesformer af opfindelsen I figur 1 vises en tryk-vakuumhøjhastighedsventil 100. Højre side af figuren viser en trykudligningsventil 1 ifølge en udførelsesform af opfindelsen. Venstre side af tegningen omfatter en vakuumdel af denne ventil 100 og udgør ikke en del af 10 opfindelsen.Embodiments of the Invention Figure 1 shows a pressure vacuum high speed valve 100. The right side of the figure shows a pressure equalization valve 1 according to an embodiment of the invention. The left side of the drawing comprises a vacuum portion of this valve 100 and does not form part of the invention.
Det skal understreges at trykudligningsventilen 1 ifølge opfindelsen kan anvendes i kombination med en sådan vakuumventil eller kan udgøre en separat enhed.It should be emphasized that the pressure equalizing valve 1 according to the invention can be used in combination with such a vacuum valve or can constitute a separate unit.
15 Trykudligningsventilen 1 omfatter et hus 10 med et ventilsæde 20, og et ventilelement 30 der er anbragt til translationsbevægelse langs en central længdeakse A af ventilhuset 10 mellem en lukket position hvor ventilelementet 30 støder op til ventilsædet, og en åben position hvor ventileiementet 30 bevæges væk fra ventilsædet 20 for at tilvejebringe en udstrømningsåbning til en gas som 20 strømmer gennem ventilhuset. Ventilhuset 10 har en første indløbsende 11 der er egnet til montering pa et lukket rum la, såsom en tank, eller på rør lb der står i forbindelse med et sådant lukket rum, som det fremgår af fig. 3. Ventilhuset 10 har endvidere en udløbsende 12 der er anbragt diametrisk ved siden af indløbsenden 11 langs aksen A på huset 10. Ventilsædet 20 er anbragt på 25 udløbsenden 12.The pressure equalizing valve 1 comprises a housing 10 with a valve seat 20 and a valve element 30 arranged for translational movement along a central longitudinal axis A of the valve housing 10 between a closed position where the valve element 30 abuts the valve seat and an open position where the valve element 30 moves away. from the valve seat 20 to provide an outflow opening to a gas flowing 20 through the valve body. The valve housing 10 has a first inlet end 11 suitable for mounting to a closed compartment 1a, such as a tank, or to pipe 1b connected to such a closed compartment as shown in FIG. 3. The valve housing 10 further has an outlet end 12 arranged diametrically adjacent the inlet end 11 along the axis A of the housing 10. The valve seat 20 is arranged on the outlet end 12.
Trykudligningsventilen 1 er beregnet til at blive monteret med udløbsenden 12 vendende opad og indløbsenden 11 vendende nedad i forhold til tyngdekraften, således at den centrale længdeakse er placeret opretstående eller vertikalt.The pressure equalizing valve 1 is intended to be mounted with the outlet end 12 facing upwards and the inlet end 11 facing downward with respect to gravity such that the central longitudinal axis is located upright or vertically.
3030
Ventilhuset 10 har en i det væsentlige ensartet indvendig bredde wl i en retning der er vinkelret på den langstrakte akse fra indløbsenden 11 til udløbsenden 12 set i et hvilket som helst snit gennem ventilhuset 10 gennem midteraksen A.The valve housing 10 has a substantially uniform internal width wl in a direction perpendicular to the elongate axis from the inlet end 11 to the outlet end 12 seen in any section through the valve housing 10 through the center axis A.
Huset 10 danner fortrinsvis et cylindrisk indvendigt rum 16, således at wl er en 35 diameter af et cirkulært tværsnit af rummet 16 vinkelret på den centrale DK 177019 B1 6 længdeakse A. Det indvendige rum 16 kan imidlertid have en anden tværsnitsform, fx ottekantet eller andre polygonale former.The housing 10 preferably forms a cylindrical interior space 16 such that w1 is a diameter of a circular cross section of the space 16 perpendicular to the central longitudinal axis A. However, the interior space 16 may have a different cross-sectional shape, e.g. octagonal or other polygonal shapes.
Med i det væsentlige ensartet bredde menes at bredden kan variere på grund af 5 produktionstolerancer og også at der kan være tilvejebragt rørindløb eller -udløb, vinduer 17 osv. i den indvendige væg der definerer det indvendige rum 16.By substantially uniform width is meant that the width may vary due to 5 production tolerances and also that pipe inlets or outlets, windows 17, etc. may be provided in the interior wall defining the interior space 16.
Ventilsædet 20 der danner udløbet fra ventilen 1, har en bredde w2 i et snit der indbefatter den centrale længdeakse A og i en retning vinkelret derpå.The valve seat 20 forming the outlet of the valve 1 has a width w2 in a section including the central longitudinal axis A and in a direction perpendicular thereto.
10 Ventilsædet 20 er fortrinsvis cirkulært; idet bredden w2 er en diameter. Bredden w2 af ventilsædet 20 er fortrinsvis den samme eller kun lidt mindre end bredden wl af huset 10's indvendige rum 16.The valve seat 20 is preferably circular; the width w2 being a diameter. The width w2 of the valve seat 20 is preferably the same or only slightly smaller than the width w1 of the interior space 16 of the housing 10.
Et ventilelement 30 er anbragt til at samvirke med ventilsædet 20 i ventilens 15 lukkede position. Ventilelementet 30 er placeret på ydersiden af det indvendige rum 16, og er anbragt til translationsbevægelse langs midteraksen A, mellem en lukket position (se fig. 1 og 2) hvor en del af ventilelementet 30’s nedre side samvirker med ventilsæde 20, og en åben position (ikke vist) hvor ventilelementet 30 er flyttet væk fra ventilsædet 20 til dannelse af en 20 udstrømningsåbning hvorigennem en gas kan undslippe.A valve member 30 is arranged to cooperate with the valve seat 20 in the closed position of the valve 15. The valve member 30 is located on the outside of the interior space 16, and is arranged for translation movement along the center axis A, between a closed position (see Figs. 1 and 2) where a portion of the lower side of the valve member 30 interacts with valve seat 20, and an open position. (not shown) where the valve member 30 is moved away from the valve seat 20 to form a 20 outlet opening through which a gas can escape.
Ventilelementet kan monteres på en aksel 61 der er udformet langs husets akse A, idet akslen 60 er anbragt forskydeligt i forhold til holdeorgan 18, 19 der er udformet i forhold til ventilsædet 20 og/eller huset 10. En stopanordning 65 er 25 udformet på akslen 61 over for ventitelementet 30 for at begrænse åbningen af ventilen 1, fx ved at stopanordningen støder op til holdeelement 19 eller ved hjælp af andre egnede organer der er tilvejebragt i huset 10.The valve member may be mounted on a shaft 61 formed along the axis A of the housing, the shaft 60 being slidably disposed relative to holding means 18, 19 formed relative to the valve seat 20 and / or the housing 10. A stop device 65 is formed on the shaft 61 to the valve member 30 to restrict the opening of the valve 1, for example, by the stop device adjacent to the holding member 19 or by other suitable means provided in the housing 10.
Et flowrør 50 er tilvejebragt på akslen 61, idet flowrøret er anbragt i huset 10's 30 indvendige rum 16. Akslen 61 danner således en forbindelse 60 mellem ventilelementet 30 og flowrøret 50. Denne forbindelse er fikseret, således at flowrøret, forbindelsen 60 (i denne udførelsesform akslen 61) og ventilelementet 30 er anbragt forskydeligt som en enkelt enhed eller et enkelt aggregat, selv om de til fremstillingsformål kan være udformet som individuelle 35 dele der forbindes under fremstillingen.A flow tube 50 is provided on the shaft 61, the flow tube being disposed in the interior space 16. The shaft 61 thus forms a connection 60 between the valve member 30 and the flow tube 50. This connection is fixed so that the flow tube, the connection 60 (in this embodiment). shaft 61) and valve member 30 are displaceably disposed as a single unit or assembly, although for manufacturing purposes they may be formed as individual parts 35 connected during manufacture.
DK 177019 B1 7DK 177019 B1 7
Andre måder til tilvejebringelse og føring af ventilelementet 30's translationsbevægelse kan arrangeres, fx ved hjælp af styreskinner udenpå det indvendige rum 16. Forbindelsen 60 mellem flowrøret 50 og ventilelementet 30 kan ligeledes være adskilt (ikke vist).Other means of providing and guiding the translational movement of the valve member 30 may be arranged, for example, by means of guide rails outside the interior space 16. The connection 60 between the flow tube 50 and the valve member 30 may also be separated (not shown).
55
Flowrøret 50 er anbragt mellem indløbsenden 11 og udløbsenden 12. Det haren tredje udvendig bredde w3 der er vinkelret på midteraksen A i et tværsnit langs midteraksen A, og en højde h der er defineret mellem en første ende 51 som vender mod indløbsenden 11, og en anden ende 52 der vender mod 10 udløbsenden 12.The flow tube 50 is disposed between the inlet end 11 and the outlet end 12. It has a third outer width w3 which is perpendicular to the center axis A in a cross section along the center axis A, and a height h defined between a first end 51 facing the inlet end 11 and a second end 52 facing 10 outlet end 12.
Flowrøret 50 harThe flow tube 50 has
Organ 40 til tilvejebringelse af en modstandsevne mod åbning af ventilen er 15 tilvejebragt mellem huset 10 og aggregatet bestående af ventilelementet 30, forbindelsen 60 og flowrøret 50.Means 40 for providing a resistance to opening the valve are provided between the housing 10 and the assembly consisting of the valve member 30, the connection 60 and the flow tube 50.
Et sådant organ 40 kan tilvejebringes i ventilelementet 30 i form af en magnet eller et magnetiserbart legeme der er anbragt til at samvirke med en magnet eller 20 et magnetiserbart legeme der er dannet i eller forbundet med huset 10. Parret danner et organ til tilvejebringelse af en nedadgående (i forhold til den tilsigtede anvendelse) anlægsskraft Fc der indeholder bidrag fra ventilelementet 30's masse, forbindelsen 60's masse, enten magnetens eller det magnetiserbare legemes masse, afhængigt af hvilken af disse dele er monteret på 25 forbindelsen 60/ventilelementet 30, og fra tiltrækningskraften Fm mellem magneten og det magnetiserbare legeme. Tilstødningskraften Fc skal således forstås som den kraft der holder trykventilen lukket, dvs. trykventilens lukkekraft.Such a member 40 may be provided in the valve member 30 in the form of a magnet or magnetizable body disposed to cooperate with a magnet or a magnetizable body formed in or connected to the housing 10. The pair forms a means for providing a downward (relative to the intended use) abutment force Fc containing contributions from the mass of the valve member 30, the mass of the connection 60, either the mass of the magnet or the magnetizable body, depending on which of these parts is mounted on the connection 60 / the valve member 30, and from the attracting force Fm between the magnet and the magnetizable body. Thus, the connecting force Fc is to be understood as the force holding the pressure valve closed, ie. the closing force of the pressure valve.
Det magnetiserbare legeme er konfigureret til at kunne samvirke med magneten i 30 trykventilen l's lukkede tilstand. Det foretrækkes at magneten og det magnetiserbare legeme er placeret i området ved udløbsenden 11 når der er behov for at opnå regelmæssig adgang til magneten.The magnetizable body is configured to cooperate with the magnet in the closed state of the pressure valve 1. It is preferred that the magnet and magnetizable body be located in the region at the outlet end 11 when regular access to the magnet is needed.
DK 177019 B1 8DK 177019 B1 8
Magneten og det magnetiserbare legeme kan dog alternativt monteres i forbindelse med forbindelsen 60 ved den ende der er placeret i det indvendige rum 16 væk fra/over for ventilelementet 30, under flowrøret 50.Alternatively, however, the magnet and magnetizable body may be mounted in conjunction with the connection 60 at the end located in the interior space 16 away from / opposite the valve member 30, below the flow tube 50.
Det kan enten være en permanent magnet eller fx en elektromagnet.It can be either a permanent magnet or, for example, an electromagnet.
55
Hvis trykket stiger til over atmosfærisk tryk i det lukkede rum, vil et sådant tryk på grund af mellemrummet mellem flowrøret og huset 10's indvendige væg også regere i rummet mellem flowrøret 50 og ventilelementet 30. Trykket i dette rum er dermed lig trykket i det lukkede rum (tank), og trykket påvirker flowrøret 50's 10 topflade og bundflade med den samme kraft. Så længe det superatmosfæriske tryk ikke fremkalder en opadgående kraft på ventilelementet 30 der overskrider trykventilens lukkekraft Fc, vil trykventilen forblive i lukket tilstand. Den opadgående kraft på ventilelementet 30 kan bestemmes som det superatmosfæriske tryk i beholderen multipliceret med åbningsområdet der er 15 defineret af ventilsædet 20.If the pressure rises above atmospheric pressure in the closed space, such pressure due to the gap between the flow tube and the inner wall of the housing 10 will also prevail in the space between the flow tube 50 and the valve element 30. The pressure in this space is thus equal to the pressure in the closed space. (tank) and the pressure affects the top surface and bottom surface of the flow tube 50 with the same force. As long as the superatmospheric pressure does not produce an upward force on the valve member 30 exceeding the closing force Fc of the pressure valve, the pressure valve will remain in the closed state. The upward force on the valve member 30 can be determined as the superatmospheric pressure in the vessel multiplied by the opening area 15 defined by the valve seat 20.
Når det superatmosfæriske tryk overstiger trykudligningsventilens lukkekraft Fc, åbner trykudligningsventiien. Gasudstrømningen bevirker at trykket på den overflade af flowrøret 50 der vender mod udløbsenden 12, falder.When the superatmospheric pressure exceeds the closing force of the pressure relief valve Fc, the pressure relief valve opens. The gas outflow causes the pressure on the surface of the flow pipe 50 facing the outlet end 12 to decrease.
20 Ventilelementet 30's opadgående bevægelse mod trykudligningsventilen l's helt åbne position styres derefter i et vist omfang af den kraft som udøves af gasstrømmen på flowrøret 50's bundflade og den gas der passerer over flowrørets udvendige sidevæg. Den første påvirkning kan bestemmes som beholderens superatmosfæriske tryk multipliceret med det område der er defineret af 25 flowrørets tværsnitareal. Gassens løftekraft på flowrøret stiger, og flowrøret 50's og dermed ventilelementet 30's bevægelseshastighed stiger i en retning mod trykventilens helt åbne tilstand, hvilket således hjælper med at holde ventilelementet 30 "flydende".The upward movement of the valve member 30 towards the fully open position of the pressure relief valve 1 is then controlled to a certain extent by the force exerted by the gas flow on the bottom surface of the flow tube 50 and the gas passing over the outer side wall of the flow tube. The first impact can be determined as the superatmospheric pressure of the container multiplied by the area defined by the cross-sectional area of the flow tube. The lifting force of the gas on the flow tube increases, and the velocity of flow of the flow tube 50 and thus the valve element 30 increases in a direction towards the fully open state of the pressure valve, thus helping to keep the valve element 30 "liquid".
30 Ventilelementet 30 holdes i den åbne position af gasstrømmen. Den nedadgående kraft på ventilelementet 30 indeholder bidrag fra ventilelementet 30's masse, forbindelsen 60's masse, enten magnetens eller det magnetiserbare legemes masse, afhængigt af hvilken af de to dele er monteret på forbindelsen 60/ventilelementet 30. Tiltrækningskraften Fm mellem magneten og DK 177019 B1 9 det magnetiserbare legeme bidrager ikke væsentligt så snart ventilelementet 30 har flyttet sig lidt væk fra den position der er vist i fig, 1 og 2.The valve member 30 is held in the open position by the gas flow. The downward force on the valve member 30 contains contributions from the mass of the valve member 30, the mass of the connection 60, either the mass of the magnet or the magnetizable body, depending on which of the two parts is mounted on the connection 60 / the valve member 30. The force of attraction Fm between the magnet and DK 177019 B1 9 the magnetizable body does not contribute substantially as soon as the valve member 30 has moved slightly away from the position shown in Figs. 1 and 2.
Eksperimenter har vist at hvis flowrøret 50's højde h er lig med eller større end 5 flowrøret 50's tredje bredde w3, vil flowrøret bevirke at ventilelementet 30 vil "flyde" i gasstrømmen, hvorved fænomenet hamring/oscillation undgås.Experiments have shown that if the height h of the flow tube 50 is equal to or greater than the third width w3 of the flow tube 50, the flow tube will cause the valve member 30 to "flow" into the gas flow, avoiding the phenomenon of hammering / oscillation.
Flowrøret 50's tredje bredde w3 er fortrinsvis mindre end den anden bredde w2 af ventilsædet 20 der åbner pi en sådan måde at flowrørets tværsnitareal er mindre 10 end tværsnitarealet af ventilsædet 20's åbning. Flowrøret monteres således nemt i huset 10 under fremstilling og også i forbindelse med vedligeholdelse og/eller reparation.The third width w3 of the flow tube 50 is preferably smaller than the second width w2 of the valve seat 20 which opens in such a way that the cross sectional area of the flow tube is less than the cross sectional area of the opening of the valve seat 20. The flow pipe is thus easily mounted in the housing 10 during manufacture and also in connection with maintenance and / or repair.
Flowrøret 50's tredje bredde w3 er fortrinsvis mellem 60% og 90% af 15 ventilhuset 10's første indvendige bredde wl, hvorved der tilvejebringes et tilstrækkeligt mellemrum mellem flowrøret og huset 10's indvendige væg.The third width w3 of the flow tube 50 is preferably between 60% and 90% of the first internal width w1 of the valve housing 10, thereby providing a sufficient space between the flow tube and the interior wall of the housing 10.
I en første foretrukket udførelsesform er flowrøret 50's tredje bredde w3 80% af ventilhuset 10's første indvendige bredde wl.In a first preferred embodiment, the third width w3 of the flow tube 50 is 80% of the first internal width w1 of the valve body 10.
2020
Som det fremgår af figurerne, har flowrøret 50 en ensartet bredde w3 fra den første ende 51 der vender mod indløbsenden 11, og den anden ende 52 der vender mod udløbsenden 12.As can be seen in the figures, the flow tube 50 has a uniform width w3 from the first end 51 facing the inlet end 11 and the second end 52 facing the outlet end 12.
25 Ventilelementet 30 er fortrinsvis formet således at det kan opfange en gasstrøm gennem ventilen 1, når den strømmer ud forbi ventilsædet 20. Dette kan opnås ved at ventilelementet udformes dråbeformet eller konusformet (fig, 1 og 2). En vertikal strøm af den udstrømmende gas kan således opnås.The valve member 30 is preferably shaped such that it can intercept a gas flow through the valve 1 as it flows past the valve seat 20. This can be achieved by forming the valve member drop-shaped or cone-shaped (Figs. 1 and 2). Thus, a vertical flow of the effluent gas can be obtained.
30 En trykudligningsventil (1) ifølge et hvilket som helst af kravene 1-8, hvor ventilhusets (10) første indvendige bredde (wl) er 100 mm, flowrørets (50) tredje bredde (w3) er 80 mm diameter og den anden bredde (w2) af ventilsædets (20) åbning er 90 mm.A pressure relief valve (1) according to any one of claims 1-8, wherein the first inner width (wl) of the valve housing (10) is 100 mm, the third width (w3) of the flow tube (50) is 80 mm in diameter and the second width ( w2) of the opening of the valve seat (20) is 90 mm.
DK 177019 B1 10DK 177019 B1 10
Som vist i figuren kan flowrøret 50 være hult. I fig. 1 og 2 er dette tilvejebragt af et hulrum i bunden af flowrøret men kan også være tilvejebragt af et opadvendende hulrum eller et lukket hulrum i flowrøret 50. Ved et hult flowrør opnås det at flowrørets masse kan justeres til at tilvejebringe optimal betjening af 5 ventilen 1. De ovennævnte bestemmelser sætter grænser for de materialer der kan anvendes til delene af en sådan ventil. Det hule flowrør muliggør således at der kan opnås en vis højde h af flowrøret uden nødvendigvis at have for stor masse.As shown in the figure, the flow tube 50 may be hollow. In FIG. 1 and 2, this is provided by a cavity at the bottom of the flow tube but may also be provided by an upwardly extending cavity or a closed cavity in flow tube 50. In a hollow flow tube, the mass of the flow tube can be adjusted to provide optimal operation of the valve 1. The foregoing provisions limit the materials which may be used for the parts of such a valve. The hollow flow tube thus allows a certain height h of the flow tube to be obtained without necessarily having too much mass.
10 Flowrøret kan være udformet i rustfrit stål.10 The flow tube may be made of stainless steel.
Afstanden d mellem kontaktoverfladen 31 mellem ventilelementet 30 og ventilsædet 20 og flowrøret 50's anden ende 52 er anbragt således at flowrøret 50's anden ende 52 ved ventilen l's åbne tilstand er mindst 15 mm, 15 såsom mellem 25-30 mm.The distance d between the contact surface 31 between the valve member 30 and the valve seat 20 and the other end 52 of the flow tube 50 is arranged so that the second end 52 of the flow tube 50 at the open state of the valve 1 is at least 15 mm, such as between 25-30 mm.
I én udførelsesform er huset 10's indvendige diameter 100 mm, flowrøret 50's diameter er 80 mm, og ventilsædets åbning er 90 mm. Massen af aggregatet der består af flowrøret og ventilelementet, kan være 4,3 kg, 4,6 kg eller 4,7 kg.In one embodiment, the inner diameter of the housing 10 is 100 mm, the diameter of the flow tube 50 is 80 mm, and the opening of the valve seat is 90 mm. The mass of the assembly consisting of the flow tube and the valve element can be 4.3 kg, 4.6 kg or 4.7 kg.
2020
Den sidstnævnte udførelsesform er blevet testet og har vist sig at eliminere fænomenet hamring. Testresultatet er illustreret i fig. 4.The latter embodiment has been tested and has been shown to eliminate the phenomenon of hammering. The test result is illustrated in FIG. 4th
Selv om den foreliggende opfindelse er blevet beskrevet i forbindelse med de 25 specificerede udførelsesformer, skal den ikke fortolkes som på nogen måde at være begrænset til de givne eksempler. Omfanget af den foreliggende opfindelse er defineret i det ledsagende sæt krav. Inden for kravenes kontekst udelukker udtrykkene "omfattende" eller "omfatter" ikke andre mulige elementer eller trin.Although the present invention has been described in connection with the 25 embodiments specified, it should not be construed as in any way limited to the examples given. The scope of the present invention is defined in the accompanying set of claims. Within the context of the claims, the terms "comprehensive" or "include" do not exclude other possible elements or steps.
Nævnte henvisninger, såsom "en" eller "et" osv., skal heller ikke fortolkes som om 30 en flertalsform udelukkes. Anvendelsen af henvisningstegn i kravene i forhold til elementer der er angivet i figurerne, skal heller ikke fortolkes som værende begrænsende for opfindelsens omfang. Individuelle kendetegn som er nævnt i forskellige krav kan endvidere muligvis med fordel kombineres, og at disse kendetegn er nævnt i forskellige krav udelukker ikke at en kombination af 35 kendetegn ikke er mulig og fordelagtig.Also, such references, such as "one" or "one", etc., should not be interpreted as excluding a plural form. Also, the use of reference characters in the claims in relation to elements set forth in the figures is not to be construed as limiting the scope of the invention. Furthermore, individual characteristics mentioned in different claims may advantageously be combined and the fact that these characteristics are mentioned in different claims does not preclude a combination of characteristics not being possible and advantageous.
Claims (11)
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DKPA200701396A DK177019B1 (en) | 2007-09-27 | 2007-09-27 | A pressure relief valve |
PCT/DK2008/050234 WO2009039857A1 (en) | 2007-09-27 | 2008-09-26 | Pressure relief valve |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DKPA200701396A DK177019B1 (en) | 2007-09-27 | 2007-09-27 | A pressure relief valve |
DK200701396 | 2007-09-27 |
Publications (2)
Publication Number | Publication Date |
---|---|
DK200701396A DK200701396A (en) | 2009-03-28 |
DK177019B1 true DK177019B1 (en) | 2011-01-03 |
Family
ID=40259330
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
DKPA200701396A DK177019B1 (en) | 2007-09-27 | 2007-09-27 | A pressure relief valve |
Country Status (2)
Country | Link |
---|---|
DK (1) | DK177019B1 (en) |
WO (1) | WO2009039857A1 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP6112315B2 (en) | 2011-12-09 | 2017-04-12 | プレス−ヴァク エンジニアリング アーペーエス | Pressure relief valve |
WO2014012967A1 (en) | 2012-07-18 | 2014-01-23 | Pres-Vac Engineering Aps | A pressure relief valve |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB841730A (en) * | 1958-01-10 | 1960-07-20 | Integral Ltd | Improvements in relief valves |
DK171444B1 (en) * | 1994-07-08 | 1996-10-28 | Emil Aarestrup Soerensen | Pressure relief valve for pressure relief between a closed room and the ambient atmosphere |
NL1002502C2 (en) * | 1996-03-01 | 1997-09-03 | Ide Albert Van Der Velde | Flame-resistant pressure equalization valve. |
JPH10299925A (en) * | 1997-04-23 | 1998-11-13 | Zexel Corp | Pressure control valve |
DE29713295U1 (en) * | 1997-07-25 | 1997-10-16 | Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München | Safety valve for high pressure hydraulics |
-
2007
- 2007-09-27 DK DKPA200701396A patent/DK177019B1/en not_active IP Right Cessation
-
2008
- 2008-09-26 WO PCT/DK2008/050234 patent/WO2009039857A1/en active Application Filing
Also Published As
Publication number | Publication date |
---|---|
WO2009039857A1 (en) | 2009-04-02 |
DK200701396A (en) | 2009-03-28 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
KR101189341B1 (en) | Internal tank gas pressure control valve | |
JP6666095B2 (en) | Valve with small vessel entry diameter | |
EP1514607A2 (en) | Inverted dispensing pump | |
DK177019B1 (en) | A pressure relief valve | |
EP2043922A4 (en) | Spout for ensuring evacuation of a flexible container | |
JP2013504725A (en) | Ventilation valve for cargo tank | |
AR034133A1 (en) | AUTOMATIC CLOSURE FOR ELASTIC DEFORMATION CONTAINERS | |
JP6295499B2 (en) | Pressure release valve | |
JP4282326B2 (en) | Pressure valve | |
JP6112315B2 (en) | Pressure relief valve | |
JP2013231571A (en) | Expansion valve | |
RU2013145711A (en) | AUTOMATIC GAS OUTLET VALVE | |
US9249897B2 (en) | Double action float valve | |
JP6130596B2 (en) | Floating structure | |
US8567647B2 (en) | Multifunctional seal device for a valve for a drinking receptacle | |
US2598409A (en) | Sand valve | |
DK2776747T3 (en) | Vent valve for cargo tanks | |
EP3538798B1 (en) | Vacuum valve for cargo tanks in, for instance, oil tankers | |
US941895A (en) | Tank. | |
US788666A (en) | Automatic stock-fountain. | |
US2587943A (en) | Pressure-vacuum control valve | |
US1223190A (en) | Attachment for vapor-heating systems. | |
CN103335161A (en) | Vacuum suppressor | |
US629464A (en) | Outlet-valve for water-tanks. | |
KR20140106202A (en) | The safety valve using elastic force of the wire |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PBP | Patent lapsed |
Effective date: 20230927 |