CA1306926C - Impact resistant pressure relief valve - Google Patents

Impact resistant pressure relief valve

Info

Publication number
CA1306926C
CA1306926C CA 588004 CA588004A CA1306926C CA 1306926 C CA1306926 C CA 1306926C CA 588004 CA588004 CA 588004 CA 588004 A CA588004 A CA 588004A CA 1306926 C CA1306926 C CA 1306926C
Authority
CA
Canada
Prior art keywords
disc
valve
valve seat
disc holder
holder
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
CA 588004
Other languages
French (fr)
Inventor
John E. Fain, Jr.
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Dresser Industries Inc
Original Assignee
Dresser Industries Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Dresser Industries Inc filed Critical Dresser Industries Inc
Application granted granted Critical
Publication of CA1306926C publication Critical patent/CA1306926C/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16KVALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/02Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with screw-spindle
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16KVALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/0433Safety 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
    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10STECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S137/00Fluid handling
    • Y10S137/904Cushion check valves
    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10TTECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00Fluid handling
    • Y10T137/7722Line condition change responsive valves
    • Y10T137/7738Pop valves
    • Y10T137/7743Lost motion between pop pressure reactor and valve

Abstract

IMPACT RESISTANT PRESSURE RELIEF VALVE

ABSTRACT
An impact resistant pressure operated relief valve comprising a valve body having an exhaust port and a nozzle assembly having a flow passage which terminates in an opening surrounded by an annular valve seat. A
disc holder in the valve body is slidably disposed between a closed position abuting the valve seat, thus closing the nozzle passage and a second position in which the disc holder is displaced from the valve seat, thus opening the valve port to the nozzle passage. A
compression spring forces the disc holder to the normally closed position. The lower portion of the disc holder is provided with a valve disc having a facing surface which is adapted to contact the valve seat in the closed position. The invention further comprises compressible shock absorber means interposed between the disc and the disc holder. The shock absorber functions to lessen the shock forces involved when the valve disc impacts upon the valve seat at closing.
This permits the use of a narrow valve seat which provides a high unit load on between the disc and the valve seat and achieves a high degree of seat tightness.

Description

IMPACT RESISTANT PRESSURE RELIEF VALVE

TECHNICAL FIELD
This invention rel~tes to pressure rellef valves and more partlcularly to lmpac~ resistan high pressure rellef valves.

~l3~

sACxGRouND
Pressure rellef valve~ ~re used ln many lndustrlal appllcatlons to prevent plant operatlng systems from reaching dangerously high pressures. Such valves include a nozzle assembly havlng a valve seat whlch is normally closed by a valve member slldably dlsposed ln the body of the valve. The valve member typlcally ls biased ln the closed positlon against the valve seat by a compression spring, by fluid pressure~ or both. Wlth the valve ln the closed posltlon, when the pressure in the nozzle passage exceeds a predetermlned set value, the valve member "pops" open and places the n~zzle passage in fluld communlcatlon wlth an exhaust port in the valve body. When the pressure ln the nozzle passage decreases by a speclfied lncremental ~mount, termed the blowdown dlfferentlal or slmply "blowdown" t to arrlve at the reseating pressure for the valve, the valve member ls agaln seated on the valve seat to ~lose the valve.
Ideally, the set polnt ~the pressure at whlch the valve opens)~ the blowdown and the reseatlng pressure should be controlled to ~lose tolerances ln order to ensure the safety of personnel and equlpment in the viclnlty of the hlgh pressure plant operatlon. The blowdown pressure dlfferentlal can be regulated by means of a secondary annular orlfice defined by means of a valve member skirt surroundin~ an ad~ustment rln~ on the nozzle assembly. For a ~iven set pressure, the blowdown can be lncreased by moving the ad~ustment rlng upward in the dlrectlon of the valva member, thus decreas~ng the . cross sectional ~rea of the ~econdary annular orlfice.
Another lmport~nt consideration ls seat tlghtness ~n order to minlmi2e v~lve leakage, partlcularly at pressures approachi~g the set pressure of the Yalve.
Seat tightness c~n be deflned ln terms of the relati~nship ~etween the set pressure of the valve ~nd 3~

the pressure, expressed as a percentage of the set pr~ssur~, at whlch the v~lve flrst beglns to leak. Seat tlghtness can be lmproved by provlding hlghly m~chlned surfaces between the valve seat and the closure face of the valve.member. In order to provlde such a hlgh quality valve surface, lt ls ~ conventlonal pr~ctlce to face the valve member wl~h ~ hl~h].y machined replaceable dlsc formed of stainless steel or l~ke materlal. ~he dlsc ls sPcured in the valve member or Ndtsc holder~ by means of a ~dlsc reta~ner~ e.g. a spllt rlng secured ln a groovs ln a dlsc stem and ~estlrlg ~galnst an lnternal shoulder wlthln the dlsc holder.
As noted prevlously, valve leakage can be mlnimlzed by preclsion machining of the cont~cting surfaces of the valve seat and the valve member dlsG. ~hus, the contactlng surfaces of hlgh quality valves ~re machlned to a surface finish of less than three microlnches in order to achieYe posltive valve seating. Valve le~kage can also be reduced by employin~ valve seats of a relatively n3rrow width whlch offer a small ~ontact area with the disc member. Valves h~vlng ~ n~rrow valve seat are m~re precise in thelr operatlng characteristlcs than valves having wlder seats and c~n provl~e a high degree of seat tl~htness. However, the use of narrow seat valves ls limlted by the forces involved ln valve opening and closlng, partlcularly ~n a valves designed for hlgh pressure operatl~s. As ~ pr~ctlcal matter such hlgh pressure valves, valves deslgned to operate at set pressures of 1000 psl or ~bove, require valve s~ats having a width in excess of 0.8 mm., and it ls ~ot uncommon for such mlnimum seat wldths to ran~e up to 0.1 lnch or above, i.e., well ~bove 2.0 mm.
Ons technlque for achievt~g seat tlghtness ~n high pressure valves involves the use of a so-called ~s~f.t seat" valve configuration. In thls deslgn, ~ resilient `~ ~3~

seal ls provlded by means of an O-rlng s~cured ln the dlsc holder by means of a dlsc shaped O-rlng retalner.
The conformlng surfaces of the valve seat of the n~zzle and the O-rlng retainer ~re beveled with the valve seat pro;ecting outwardly from the retalner perlphery so that the metal to metal surfaces of the retalner ~nd the valve seat bear the load imposed upon the disc holder.
At the same time, contact between the outer edge of the Yalve seat in the O-rlng provldes the valve seallng functlon.
Pressure rellef valves of the type descrlbed Dbove are disclosed ln Dresser Industrles Inc.'s Catalog SRV-l ~Consolidated~ Safety Relief Vslves~ (1984), Sectlons 1 ~nd 2. Soft seat valves ~re partlcularly dlsclosed $n Sectlon 2, pages 13-15.

5 ~ 3~
SUMMARY OF THE INVENTION
In accordance with the present lnventlon, there ls provided a new pressure oper~ted rellef valve which pr~vides a hlgh degree of seat tlghtness characterlstic - of soft seat valves but wlth th~ metal to metal seallng ~unctlon of a hard seat valve provlding ~ hlgh degree of durablllty. The-pressure operatecl rellef valve of the present lnventlon comprlses ~ v~lve body havln~ an exhaust port ~nd a n~zzle ~ssembly extending lnto the valve body. The nozzle 3ssembly has a flow p~ssage which termlnates in ~ openlng exposed to the lnterlor of the valve body. An ~nular valve seat 15 formed around the noz71e opening. A dlsc: holder ls slldably disposed ln the valve body between a closed position ~5 abutlng the valve seat, thus preventing fl~d communlcatlon batween the nozzlR passage and the exhaust port, ~nd a second p~sitlon in whlch the dlsc holder is displaced from the valve seat, thus openlng the valve port to the nozzle passage. Suitable means such as a compresslon sprlng or the llke functions to bias the dlsc holder toward the cl~sed posltlon. The lower pQrtion of the disc holder ls provlded with a va~ve disc havlng a f~cing surface whlch is ~dapted to contact the valve seat. The lnvention further comprlses compressible shock absorber means lnterposed between the disc and the disc holder. The shock absorber means functlons to lessen the sho~k forces i~volved when the valve disc ~mpacts upon ~he ~alve seat at closing.
The ~onfiguratlon 1~YO1V1ng the shock absorbPr means and the annular valve se~t permits the use of a narrow valve seat, thus providlng a hlgh unlt lo~d between the dlsc and the valve seat ~nd ~chievlng a hlgh degree of seat tlghtness. Thus, the v~lve seat wldth can be no more than 0.8 mm. ~elow the wldth normally encountered ln metal to metal valve seats. Preferably Y~.
~3~

the wldth of the valve seat wlll be wlthln the range of about 0.4-0.6 mm. The v~lve seat wldth normally should be greater than 0.3 mm in order to ensure sufflclent seat strength even notwlthstandlng the use of the compressible shock absorber means.
In one embodlment of the inventlon the valve dlsc is provided with a passage extendLng between the rear and the front face of the valve dlsc. The p~ssaye termlnates at the faclng surface Ln an enlarged recess.
Fastening means havlng ~n enlarged shouldsr section which ls set 1n the recess extends through the passage ~nd is connected to the dlsc hold~3r behlnd the valve dlsc ln order to hold the valve dLsc ln place against ~he compressible shock absorber means. Preferably, when the valve is ln the closed posltlon the surface area of the disc ls greater than the surface area of the nozzle opening. When the valve ls 1n the closed posltlon a substantlal portion of the force due to ~he pressure wlthln the nozzle ls tr~nsmitted directly to the dlsc holder rather than through the shock absorber means.
In yet a further embodlment of the lnvention the v~lve disc provldes an integral fac1ng surface exposed to the nozzle ~penin~. The valv~ disc is secured to the valve holder by means of a rearwardly extendlng pedestal whlch ls lnterconnected wlth the dl5c holder to permlt relative rearward movement of the v~lve dlsc relatlve to the dlsc holder against the ~ompresslble shock a~sorber means.
2~i BRIEF DESCRIPTION OF THE DRAWINGS
FIGURE 1 ts a slde elevatlonal vlew, partly ln sectlon, lllustratlng a pressure operated release valve . embodylng the present inventlon.
FIGURE 2 ls a slde elevational view partly ln sectlon, showlng detail~ of the nozzle assembly, dlsc and dlsc holder ln one embodiment of the lnventlon.
FIGURE 3 ls a slde elevatlonal vlew partly ln section showlng the assembly of FIG~RE 2 wlth the valve ln the open posltlon.
FIGURE 4 ls a slde elevatlonal view partly ln section showlng details of an~ther embodlment o~ the lnvention.

~3~6~

DETAILED DESCRIPTION OF THE INVENI ION
Referring lnltlally to FIGURE 1 there ls illustrated a valve comprlsing ~ valve body 12 formed of a base component 14 ~nd a bonnet component 16 whlch ls secured to the base by means of nuts and studs 18 and 19. The valve body ls provlded wlth a nozzle assembly 21 whlch provldes an inlet to the valve body and an exhaust port 23 through wh:lch fluids may be expelled when the valve ls ln the open posltion. A
pass~ge 25 throu~h the nozzle assembly termlnates ln an enlarged opening 26 in valve seat 27 which, when the valve ls ln the closed position a~s show~, ~s cl~sed by valve member 28. Valve member 2a comprtses a dlsc holder 29 whlch is secured ln and slldably dispo~ed withln the gulde way 31 of gulde ~ssembly 32. The guide assembly lncludes a transverse mountlng plate 33 held in place between the base and bonnet components. The disc holder supports a disc 34 having a machined face which rests upon the valve seat 2~. Dlsc holder 2g ls provided wlth an annular skirt 36. Sklxt 36 pro~ects downwardly from the disc holder ln con~unctlon wlth an ad~ustment rlng 38 on the nozzle ~ssembly provides a secondary orifice for regulating the blowdown pressure of the valve.
The valve member 28 is blased downw~rdly to the closed position by means of a compresslon sprlng 40 lnterposed between washers 41 and ~2 whi~h ~re slid~bly mounted on the shank of a splndle 4~. Spindle 44 ls : provided at ths bottom wlth an enlarged splndle head 45 which ls seated ln ~ recess 47 at the upper end of the disc holder and is retained thereln by means of ~ split retainlng ring 48. The lower washer 41 rests upon the shoulder provlded on the splndle, and the upper w~sher 42 ls limlted ln upward movement by the bottom shoulder ~5 of an ad~usting screw 50 which is threaded within the ~3e~6~2~
g top plate of the bonnet component 16. It wlll be reco~nlzed that the compreslve force exerted by compression sprlng 40 can be ad~u~ted by movlng the ad~ustment screw up or down. Screw 50 ls held ~t the s deslred posltlon by means of an ~d~ustlng screw nut 52.
The upper end of the assembly ls ~provided wlth a cap 5~
to cover the ad~ustment screw ænd the threaded upper end of the splndle shan~.
The guide assembly plate 33 Is provlded w1th an eductor tube 55 wh~oh extends from the bonnet srea into ; the passage leading to the exhaust port. The eductor tube functlons to reduce pressure wlthln the bonnet area due to leakage of fluid past the gulde surfaces when the valve is in the open positlon. Fluld flow through the outlet port acts to lmpose a syphon effect on th~
eductor tube to wlthdraw fluld from the bonnet ~rea.
The valve components as descr~bed ~hus far are conventional and are exemplary of a typic~l valve configuratlon ln whlch the present inventlon can be ~0 utili.ed. However, lt will be recognized that other valve conflgurations to which the lnvention is applicable are known to those skllled ln the art. For example, the bonnet ~rea may be s~aled off from fluids by means of bellows located around the upper portlon of the dlsc holder, t~us elim~natlng the ne~d for an eductor tube. Reference ls made to Sectlons 1 ~nd 2 of ~he aforementloned Dresser Industries ~ Inc . Cat~log SRV-1 for a further descriptlon of various valve csnfigurations wlth respect to whlch the present ~nvention can be utlll~ed.
Turning now to Flgure 2, there ls illustrated ~n enlarged vlew, partly ln sectlon lllustrating det~lls of the n~zzle assembly ~nd corresp~nding valve member employed ln ~ne embodlment of the present lnventlon. ~n FIGURE 2, an annular shock absorber 56 ls interposad between a forward faclng lnternal shoulder 57 ln the dlsc holder 29 and a rearward facing shoulder 58 formed on the ~ack o~ the disc 34. Shock absorber 56 may be formed of a any sultable ~ompress:lble resllient materlal capable of absorbing shock forces imposed upon the face of the dlsc when the valve closes. ~y way of ex~mple the shock absorber may take the form of a standard rubber O-rlng. The operatlng face of the disc is provlded with an enlarged recess whlch ln the embodlment shown ls tapered to accommodate the conformlng surface of the head of a set screw 62. Screw 62 extends through a central passage ln disc 34 and is threadedly secured wlthin a threaded hole 64 in the disc retainer.
The flared surface of the head of set screw 62 holds the disc agalnst downward movement but it will accommodate rearward movement of the dlsc agalnst the compresslble shock absorber. Such rearward movement however is llmited by the back portlon of dlsc 66 which ultimately wlll abut against the forward faclng shoulder 67 ln the disc holder.
The nozzle passage 25 is enl~r~ed ~t lts upper end thereby ~ncreaslng the valve member area escposed to the flu~ d pressure and increasing the force on the valve member. Th~s enables the use of ~ greater sprlng force, thus improvlng the ~popping~ characterlstlcs of the valve as it opens. Wlth the ~lve in the closed position lllustratea ln Fi~ure 2, tha force imposed by th~ high pressur~ fluld at nozzle openlng 26 ls transmltted to the dlsc holder through the valve disc 34. ~he full force resultin~ from the pressure upon the disc is not transferred to the shock absorber ln the closed positlon.
W~th the valve ln the cl~sed positi~n, leakage past t~e interf~ce between thQ screw 62 and the ~ore wlthin the valve disc imposes ~ b~ck pressure upon ~he shock ~3~6 absorber element. So long as the valve remalns closed, a pressure gradlent w~ll thus be establlshed across the shock absorber element whlch wlll functlon ~s a seal ln addltlon to performlng a shock absorber functlon.
~ When the valve is closed durlng normal operatlon ~s shown ln FIGURE 2 the shoulder 67 of the disc holder rests on the s~oulder 66 of the dlsc. The s~rew 62 wlll move wlth the disc holder relatlve to the disc ~nd thus the screw head wlll pro~ect sllght~y out of the recess in the ace of the dlsc holder. ~he inlet fluld pressure ~ctlng against the seatlng surfaces ls opposed by the sprlng ~Drce exerted by the compressi~n spring 40. The force of the sprlng 40 whl~h acts to hold the dlsc 34 on the valve seat 27 is transmltted through the dlsr holder ~nd ths shock absorber element 5~O As the lnlet pressure ln nozzle passage 25 increases above the operating pressure for the system, the pressure ln the nozzle tends to equallze the sprlng force, and the forces holdlng the valve seating surfaces together approach zero. At thls point a pr~or art safety rellef valve will tend to audlbly ralieve the fluid medium past the seatlng surfaces, resulting ln a condition commonly referred to as "slmmer.~ Once the slmmerlng condltlon ls reached, a hi~her lnlet press~re ls requlred to achieve the set polnt of the valve and cause lt to pOp~
~he present invention mlnlmizes ~nd ln mo~t c~ses ~ctually eliminates the simmer. ~he ~sprlng force~ due . to the resllle~cy of the shock absorber element 56 interacts wlth the sprlng force lmposed by the compresslon spring 40 to hold the valve dlsc tlght agalnst the valve se~t Dt pressures very near to the set po~nt of the valve. For example, where ~ conventional valve might begin to show leak~ge ~t ~bout 90~ of the -35 set polnt, ~ valve conflgured ln accord2nce wlth the ~3~

present lnventlon can be expected to retaln a seat tightness even after several ~pops~ of up to ab~ut 98 of the set pressure.
Once the valve does pop open, the secondary annular orlflce ls created by the sk1rt port~on 36 of the disc holder and the ad~ustment rlng 3B. The effective cross-sectlonal area of the secondary sr~ular orifice can be regulated similarly as in the case of prior Drt valYes by threadedly ad~ustlng ring 38 up or down on the nozzle assembly. As the pressure lncreases in the secondary orifice area, the dlsc 34 and disc holder are forced into a degree of lift allowln~ the valve ~o accomplish full capaclty flow.
FIGURE ~ lllustrates the assembly of PIGURE 2 ln the open posltion after the valve has popped open. As explalned prevlously, the blowdown pressure d~fferentlal, and thus the reseat pressure can be regulated by ad~ustment of the ring 38 to deflne a desired cross sectional area of the second~ry oriflce.
When ths pressure reduces to the reseatlng point the valve will close rapidly under the actlon of the compression sprin~ 40. The sho k forces imposed upon the valve seat and the valve disc are reduced by the functlon of the shock absorber element. In additlon, the design of the secondary annular orlflce ls su~h that ~s the valve b~g~n to ~lose, the effectlve cross-sectlo~al ~rea of the secondsry orifice decreases to provlde ~ cushlonlng effect upon the valve closure~
This effect also acts together wlth the shock absorber to reduce some of the hammerlng force ~t the valvs seat.
The shock absorber enables tha width of the valve se~t, as indlcated by dimenslon ~dn in ~IGURE 3, to be conflgured to a very ~arrow dlmenslon which tends to promote a hlgh unit load upon the valve seat and provide ~5 for a tlght seat between the valve seat ~nd the actlve '".`h.
~3~

face of the dlsc 34.
Typlcally for a valve deslgned to operate at pressures above 1000 psl the seat wldth ls ~bove 0.8 mm.
In the present lnventlon the dimenslon ~d~ can be conflgured to a value of less than 0.8 mm. A preferred value for dlmenslon Nd~ 19 ~lthln the r~ge of 0.4-0.6 mm .
~I~U~E 4 lllustrates an alterna~lve embodlment of the lnventlon havtng a modifled d.lsc ~nd dlsc holder which ls useful ~here it ls desired to remove the shock absorber means from contact wlth the fluld medlum when the valve is ln the normal closed posttion. As ~hown ln FIGURE 4, the face 70 of the valve dlsc 72 is an lntegral surface so that, wlth the valve ln the closed position, shock absorber element 56 ls not exposed to the fluld medium. In thls case the disc is retalned within disc holder ~4 by means of A split ring 76 secured withln a groove 77 within the rearwardly extending pedestal 78 of the disc. An internal bore ~o within the disc holder ls provlded wlth a shoulder al upon whlch the retalner abuts pr¢venting displacement of the d~sc from the dlsc retainer. As shown in FIGURE 4, the ~isc can move rearward to the extent pe~mltted by the distance between the disc shoulder 83 and dl~c retalner shQulder 84. In this embodlment the disc retatner ls provlded wlth passages 86 through ~hlch a drift pin or other approprlate implement c~n be lnserted to blas the disc downwardly ~nd remove it from the disc holder.
Havlng descr~bed specific embodiments of the present lnvention, it will be understood that modtflcati~n thereof may ~e su~gested to those skllled ln the art, ~nd lt is lntended to cover all such modlfications ~s fall wlthin the scope of the ~ppended claims.

Claims (16)

1. In a pressure operated relief valve, the combination comprising:
(a) a valve body having an exhaust port therein;
(b) a nozzle assembly in said valve body having a flow passage therein and terminating in an opening in an annular valve seat around said flow passage, said valve seat comprising a surface having a width of less than 0.8 millimeter which is cooperative with and adapted to be contacted by the hereinafter recited planar disc facing surface;
(c) a disc holder slidably disposed in said valve body between a closed position adjacent said valve seat to close communication between said flow passage and said exhaust port and a second position in which said exhaust port is in fluid communication with said flow passage;
(d) a valve disc secured to said disc holder and having a planar facing surface;
(e) compressible shock absorber means interposed between said disc and said disc holder, and (f) a means for biasing said disc holder in the direction of said valve seat to normally hold said valve disc facing surface against and in contact with the cooperative surface of said valve seat in the closed position.
2. The combination of claim 1 wherein said valve seat has a width within the range of 0.4 - 0.6 millimeters.
3. The combination of claim 1 wherein said valve disc comprises a central pedestal extending rearwardly from the back surface of said valve disc and defining a back shoulder on said valve disc on which said compressible shock absorber means is mounted.
4. The combination of claim 3 wherein said valve disc has a passage extending through said valve disc and terminating in the facing surface of said valve disc in an enlarged recess and fastening means having an enlarged shoulder section set into said recess and extending through said passage and rigidly connected to said disc holder at the rear of said pedestal in order to hold said valve disc in place against said compressible shock absorber means.
5. The combination of claim 4 further comprising conforming shoulder surfaces on said valve disc pedestal and at the interior of said disc holder to limit rearward movement of said disc relative to said disc holder against the compressive force of said shock absorber means.
6. The combination of claim 3 wherein further comprising means to secure said valve disc to said disc holder by interconnection of said rearwardly extending pedestal with said disc holder to permit slidable rearward movement of said valve disc relative to said disc holder against said compressible shock absorber means.
7. The combination of claim 6 further comprising conforming shoulder surfaces on said valve disc pedestal and at the interior of said disc holder to limit rearward movement of said disc relative to said disc holder against the compressive force of said shock absorber means.
8. In a pressure operated relief valve, the combination comprising:
(a) a valve body having an exhaust port therein;
(b) a nozzle assembly in said valve body having a flow passage therein and terminating in an opening in an annular valve seat around said flow passage, said valve seat comprising a surface having a width of less than 0.8 millimeter which is cooperative with and adapted to he contacted by the hereinafter recited planar disc facing surface;
(c) a disc holder slidably disposed in said valve body between a closed position adjacent said valve seat to close communication between said flow passage and said exhaust port and a second position in which said exhaust port is in fluid communication with said flow passage;
(d) a valve disc secured to said disc holder having a planar facing surface adapted to contact said valve seat and a central passage in said valve disc terminating in said facing surface of said valve disc in an enlarged recess;
(e) compressible shock absorber means interposed between said disc and said disc holder;
(f) fastening means having an enlarged shoulder section set into the recess of said valve disc and exposed to said nozzle opening, said fastening means extending through said passage and being rigidly connected to said disc holder at the rear of said valve disc in order to hold said valve disc in place against said compressible shock absorber means; and (g) a means for biasing said disc holder in the direction of said valve seat to normally hold said valve disc facing surface against and in contact with the cooperative surface of said valve seat in the closed position.
9. The combination of claim 8 wherein said fastening means comprises a set screw extending through said valve disc and threadedly secured to said disc holder, said set screw having a flared head and the recess in said valve disc having a flared surface conforming to the head of said set screw.
10. The combination of claim 8 wherein said disc holder comprises a circumferential skirt member extending downwardly and defining with said nozzle assembly a secondary annular orifice.
11. The combination of claim 10 further comprising an adjusting ring threadedly secured from the external surface of said nozzle assembly to enable changes in the effective cross-section of said secondary annular orifice.
12. The combination of claim 8 wherein the valve seat has a width within the range of 0.4 - 0.6 millimeters.
13. The combination of claim 8 further comprising conforming shoulder surfaces on said valve disc rearwardly of said shock absorber means and on the interior of said disc holder to limit rearward movement of said disc relative to said disc holder against the compressive force of said shock absorber means.
14. In a pressure operated relief valve, the combination comprising:
(a) a valve body having an exhaust port therein;
(b) a nozzle assembly in said valve body having a flow passage therein and terminating in an opening in an annular valve seat around said flow passage, said valve seat comprising a surface having a width of less than 0.8 millimeter which is cooperative with and adapted to be contacted by the hereinafter recited planar disc facing surface;
(c) a disc holder slidably disposed in said valve body between a closed position adjacent said valve seat to close communication between said flow passage and said exhaust port and a second position in which said exhaust port is in fluid communication with said flow passage;
(d) a valve disc secured to said disc holder and having an integral planar facing surface adapted to contact said valve seat, a back central pedestal extending rearwardly from the back surface of said valve disc and defining an annular shoulder surface on the rear of said valve disc;
(e) compressible shock absorber means interposed between the annular shoulder surface of said disc and a corresponding shoulder surface in said disc holder;
(f) means securing said valve disc to said disc holder by interconnection of said pedestal with said disc holder to permit slidable rearward movement of said valve disc relative to said disc holder against said compressible shock absorber means; and (g) a means for biasing said disc holder in the direction of said valve seat to normally hold said valve disc facing surface against and in contact with the cooperative surface of said valve seat in the closed position.
15. The combination of claim 14 wherein the valve seat has a width within the range of 0.4 - 0.6 millimeters.
16. The combination of claim 14 further comprising conforming shoulder surfaces on said valve disc pedestal and at the interior of said disc holder to limit rearward movement of said disc relative to said disc holder against the compressive force of said shock absorber means.
CA 588004 1988-01-25 1989-01-11 Impact resistant pressure relief valve Expired - Fee Related CA1306926C (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US147,790 1988-01-25
US07/147,790 US4858642A (en) 1988-01-25 1988-01-25 Impact resistant pressure relief valve

Publications (1)

Publication Number Publication Date
CA1306926C true CA1306926C (en) 1992-09-01

Family

ID=22522909

Family Applications (1)

Application Number Title Priority Date Filing Date
CA 588004 Expired - Fee Related CA1306926C (en) 1988-01-25 1989-01-11 Impact resistant pressure relief valve

Country Status (9)

Country Link
US (1) US4858642A (en)
EP (1) EP0326509B1 (en)
JP (1) JP2631542B2 (en)
KR (1) KR0184856B1 (en)
CN (1) CN1014170B (en)
BR (1) BR8900297A (en)
CA (1) CA1306926C (en)
ES (1) ES2037992T3 (en)
MX (1) MX166355B (en)

Families Citing this family (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5744101A (en) * 1989-06-07 1998-04-28 Affymax Technologies N.V. Photolabile nucleoside protecting groups
US5064169A (en) * 1990-03-30 1991-11-12 Keystone International Holdings Corp. Shock absorbing means for flow control devices
US5011116A (en) * 1990-03-30 1991-04-30 Keystone International Holdings Corp. Shock absorbing sealing means for flow control devices
US5234023A (en) * 1992-02-27 1993-08-10 Dresser Industries Pressure relief valve with auxiliary loading device
US5370151A (en) * 1994-03-23 1994-12-06 Dresser Industries Inc. Safety valve
AT407188B (en) * 1997-07-16 2001-01-25 Hoerbiger Hydraulik VALVE
US6161571A (en) * 1999-05-14 2000-12-19 The Living Trust of Eleanor A. Taylor Modulating relief valve
US7015957B2 (en) * 2001-09-04 2006-03-21 Eastman Kodak Company Camera that downloads electronic images having metadata identifying images previously excluded from first in-first out overwriting and method
KR20050054900A (en) * 2005-05-19 2005-06-10 윤수권 Pre-fill valve with double disk
US8607818B2 (en) * 2010-05-20 2013-12-17 Dresser, Inc. Pressure relief valve
US8505572B2 (en) * 2010-12-29 2013-08-13 Dresser Inc. Pressure relief valve
DE102011005485A1 (en) * 2011-03-14 2012-09-20 Robert Bosch Gmbh Valve device for switching or metering a fluid
US20120273220A1 (en) * 2011-04-27 2012-11-01 Bp Corporation North America Inc. Pressure relief valve
DE102014200074A1 (en) * 2014-01-08 2015-07-09 Robert Bosch Gmbh Valve
CN103900810A (en) * 2014-04-16 2014-07-02 江苏二马液压元件有限公司 Durability test table for safety valve
CN105020450A (en) * 2015-06-01 2015-11-04 刘银明 Shock absorption water stop valve for branch pipeline of water suction pump
CN108278759A (en) * 2018-01-23 2018-07-13 浙江上风高科专风实业有限公司 A kind of asymmetry runner shock-wave resistant air vent valve
KR101970299B1 (en) 2018-11-06 2019-04-18 대전과학기술대학교 산학협력단 The electronic pressure switchgear
CN110671525A (en) * 2019-09-25 2020-01-10 姚炳龙 Pressure reducing and stabilizing valve
US20230088255A1 (en) * 2021-09-17 2023-03-23 Emerson Automation Solutions Final Control US LP Systems and Methods for Reducing Simmer in a Safety Relief Valve
US11614176B1 (en) 2022-08-29 2023-03-28 Prince Mohammad Bin Fahd University Relief valve device

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US587704A (en) * 1897-08-10 Valve for air or gas compressors
US353995A (en) * 1886-12-07 thomas asceoft walker
US2088666A (en) * 1937-08-03 Faucet
FR813229A (en) * 1937-05-28
US2247773A (en) * 1939-02-15 1941-07-01 Stephen M Dunn Valve
US2517858A (en) * 1947-11-29 1950-08-08 Victor W Farris Safety valve
US2643090A (en) * 1950-09-09 1953-06-23 Harjeroy Engineered Petroleum Shock absorbing check valve for hydraulic systems
US3001545A (en) * 1958-10-22 1961-09-26 Manning Maxwell & Moore Inc Spring loaded pop-action safety valves
US3872875A (en) * 1970-11-23 1975-03-25 Jr John H Raidl Relief valve isolating means
AT331602B (en) * 1973-04-24 1976-08-25 Rappoport Efim Moiseevich SAFETY VALVE
DE2422165A1 (en) * 1973-12-03 1975-06-05 Enrico Pignatelli DEVICE FOR LIMITING GAS FLOW FROM AND INTO A CONTAINER
US3854494A (en) * 1974-02-04 1974-12-17 Crosby Valve & Gage Safety valve

Also Published As

Publication number Publication date
EP0326509B1 (en) 1993-01-07
MX166355B (en) 1992-12-31
US4858642A (en) 1989-08-22
AU2849289A (en) 1989-07-27
CN1014170B (en) 1991-10-02
BR8900297A (en) 1989-09-19
AU613141B2 (en) 1991-07-25
JPH01288670A (en) 1989-11-20
KR890012112A (en) 1989-08-24
EP0326509A1 (en) 1989-08-02
CN1034987A (en) 1989-08-23
JP2631542B2 (en) 1997-07-16
KR0184856B1 (en) 1999-04-15
ES2037992T3 (en) 1993-07-01

Similar Documents

Publication Publication Date Title
CA1306926C (en) Impact resistant pressure relief valve
EP0573399B1 (en) Trim for ANSI class V shut off valves
US4721284A (en) Valve plug design
US4508140A (en) Hydraulic flow control valves
US6622752B2 (en) Pressure relief valve
US3979105A (en) Valve with improved flow passage
US4543987A (en) Relief valve
WO1996001445A1 (en) A fluid pressure regulator
JPS621505Y2 (en)
US4537384A (en) In-line check valve having combined downstream poppet support and flow control elements
US3583431A (en) Pressure relief valve
US4964423A (en) Check valve
US4685489A (en) Valve assembly and compressor modulation apparatus
US4923173A (en) Seating seal means for disc-type valve
US3887159A (en) Ported valve and sealing means therefor
US4651971A (en) Direct acting valve assembly
US3192948A (en) Ball valve with sealing capsule
US5149055A (en) Shut-off valve
US3544065A (en) Resilient annular valve seat with coaxial rigid annular member
CA2072692C (en) Fluid flow controller
US5899221A (en) Fluid pressure regulator
US4316598A (en) Balanced relief valve with novel seal
CA1301017C (en) Valve seat configuration
US5305780A (en) Pressure relief valve with auxiliary loading device
US3675896A (en) Valve including resilient seat washer with abutting rigid annular washer

Legal Events

Date Code Title Description
MKLA Lapsed