US3621875A - Pressure-actuated valve - Google Patents

Pressure-actuated valve Download PDF

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Publication number
US3621875A
US3621875A US3621875DA US3621875A US 3621875 A US3621875 A US 3621875A US 3621875D A US3621875D A US 3621875DA US 3621875 A US3621875 A US 3621875A
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US
United States
Prior art keywords
poppet
chamber
pressure
inlet
fluid
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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 - Lifetime
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English (en)
Inventor
Frank N Alexander
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Eaton Corp
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Cessna Aircraft Co
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Publication of US3621875A publication Critical patent/US3621875A/en
Assigned to EATON CORPORATION, EATON CENTER, CLEVELAND, OH 44114-2584, AN OH CORP. reassignment EATON CORPORATION, EATON CENTER, CLEVELAND, OH 44114-2584, AN OH CORP. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: CESSNA AIRCRAFT COMPANY, THE
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F16K17/04—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
    • 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
    • F16K15/00—Check valves
    • F16K15/02—Check valves with guided rigid valve members
    • F16K15/06—Check valves with guided rigid valve members with guided stems
    • F16K15/063—Check valves with guided rigid valve members with guided stems the valve being loaded by a spring
    • 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
    • F16K17/044—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 more than one spring
    • 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
    • F16K47/00—Means in valves for absorbing fluid energy
    • F16K47/01—Damping of valve members
    • F16K47/011—Damping of valve members by means of a dashpot
    • 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
    • F16K2200/00—Details of valves
    • F16K2200/30—Spring arrangements
    • F16K2200/302—Plurality of biasing means, e.g. springs, for opening or closing single valve member
    • Y—GENERAL 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7837—Direct response valves [i.e., check valve type]
    • Y10T137/785—With retarder or dashpot
    • Y—GENERAL 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7837—Direct response valves [i.e., check valve type]
    • Y10T137/7904—Reciprocating valves
    • Y10T137/7905—Plural biasing means

Definitions

  • L- 137/514 ABSTRACT A pressure-actuated relief valve is disclosed hav- [51] lint. Cl ..F16k 21/06, ing biasing means urging the poppet to a closed position which F fik 7/02 biasing means includes a damped and an undamped member [50] Field of Search 137/87, cooperating to provide fast response while controlling poppet 5145, 14, DIG. 5 oscillation.
  • the damped member includes a spring within a hydraulic dashpot and serves as a reaction seat for the un- [56] References (med damped member. Fast pressure increases compress only the UNITED STATES PATENTS undamped member while longer duration pressure signals will 898,659 9/1908 Kuehl l37/DIG.5 also wmpressthc mp d member.
  • Flow control valves of the pressure relief type are actuated in response to a predetermined increase in hydraulic pressure to regulate and maintain system pressure of a desired level.
  • such valves generally include a control member or poppet variably positioned by a hydraulic actuating pressure to meter, control and direct fluid flow to a low pressure outlet.
  • Biasing means act against the control member in opposition to the pressure forces so that the control member is positioned by the balance between the force exerted by hydraulic pressure and the biasing means.
  • a problem common to such control valves is obtaining proper response to the pressure actuating force to produce the desired control of fluid.
  • Improper action of the control member such as too slow or too fast responsive movement to the pressure applied, may result in uncontrolled oscillation, chatter, excessive flow and pressure fluctuations and generally unacceptable performance.
  • proper and acceptable performance of the control valve can be achieved.
  • the present invention is directed toward an improved biasing member construction for pressure actuated valves providing improved damping and generally better valve performance characteristics.
  • the improved damping characteristics produce stable operation, fast response and reduce operational noise of the valve without introducing sluggishness or insensitivity in its operation.
  • the invention contemplates at least a two-stage resilient biasing member within the valve arranged to exert a biasing closing force on the control member or poppet.
  • One stage of the biasing member is damped while the other is undamped. Compression of the damped stage requires longer duration pressure signals, while the other undamped stage is capable of moving quickly in response to pressure surges acting on the control member.
  • a relief valve is provided with two springs which are compactly arranged with the damped spring acting through and with the undamped spring to bias the control member to a closed position. Movement of the control member through pressure actuation sequentially causes compression of the undamped spring and then the damped spring.
  • the damped spring acts as the seat or reaction member to the undamped spring during its compression. Damping of the one spring is achieved through the use of a hydraulic dashpot.
  • a primary advantage of my invention resides in providing a relief valve which retains the responsiveness of a valve having undamped biasing while eliminating the instability normally associated with undamped biasing means.
  • the valve of the present invention has particular application in systems where the exhaust or discharge is at some predetermined back pressure above atmospheric.
  • the drawing illustrates a portion of a fluid pressure device having a high pressure chamber 11 and a low pressure fluid return chamber 12 communicating with a reservoir of low pressure fluid.
  • 10 may be a portion of a control valve having supply duct 11 and return passageway 12.
  • Cartridge-type relief valve 13 embodying the present invention is threadably secured to the device 10 and extends through bore 14 to hydraulically communicate with chambers 11 and 12 and functions to selectively divert fluid from chamber 11 to chamber 12 and prevent overpressurization ofchamber l1.
  • Relief valve 13 has a two-piece housing including casing 15 which receives closure member 16. Interior bores 17 and 18 are provided in members 15 and 16, respectively. Cross bores 19 and 20 in valve housing sections 15 and 16 are open to the high and low pressure chambers 11 and 12, respectively, and serve as inlet and outlet openings through the valve.
  • Seat 22 held within closure 16 by snap ring 21 is seat 22 which is bored to sealingly receive the frustoconical outer surface 27 of poppet 23 in the valve closed position as illustrated.
  • Poppet 23 is movable within internal bore 17 of member 16 and has a central bore 24 extending through the poppet. The left end of poppet 23 is provided with outlet openings 25 which place bores 24 and 18 incommunication and permit selective communication between chambers 11 and 12 through bore 24 and opening 25.
  • Appropriate sealing members 26 retard leakage from chamber 11.
  • the improved biasing means 28 of the present invention comprise two helical compression springs 29 and 30 situated in passage 18 and sequentially arranged to extend between the closed end of cartridge 15 and poppet 23.
  • lnteriorly located pin 31 having an enlarged diameter flange 32 is interposed between the springs, and a conically ended body portion extends forwardly toward poppet 23.
  • the conical end on pin 31 acts as a flow deflector to assist and redirect fluid flowing from chamber 11 axially through bore 24, outwardly through the coils of spring 29, which compresses and reduces flow area as the poppet opens, and notches 25 to crossbores 20 and chamber 12.
  • Flange 32 is circular conforming to bore 18 and defines at its periphery, in cooperation with the internal diameter of bore 18, an annular restriction at 35.
  • Two variable volume fluid chambers 33 and 34 are in communication through restricted passage 35 formed between flange 32 and the wall of bore 18.
  • a suflicient number of outlet apertures 20 are included in cartridge 15 so that chamber 33 openly communicates with low pressure passage 12.
  • fluid can escape from chamber 34 only through annular restriction 35, thereby creating a hydraulic damping chamber or dashpot 34 limiting the speed of compression of spring 30 and speed of movement of poppet 23.
  • Annular restriction 35 is sized to provide the desired damping characteristics and speed of movement of poppet 23.
  • the restricted hydraulic communication between chambers 33 and 34 can be provided through other constructions such as one or more properly sized orifice holes extending through pin 31, or orifices directly communicating chamber 34 with low pressure passage 12.
  • springs 29 and 30 are set to a predetermined compression by inclusion of one or more shims 36 to establish the desired closing bias force upon poppet 23.
  • the force exerted on poppet 23 overcomes the bias of springs 29 and 30 and moves the poppet leftwardly individually, an open position.
  • spring 29 compresses slightly against flange 32 as the dashpot chamber 34 prevents sudden and immediate compression of spring 30.
  • spring 29 exhibits a relatively high spring gradient due to its relatively short length (that is, a closing force increasing very rapidly with spring compression) so that this initial movement, and the consequent flow relieved from chamber 11, is limited.
  • the spring biasing and damping means permit rapid, but limited, undamped movement of the poppet control member as well as a hydraulically damped and well controlled major opening response of poppet 23.
  • the damping afforded by chamber 34 and the dual spring arrangement permits valve 13 to relieve large flows from chamber 11 without inducing poppet instability, pressure overshoot and oscillation and attendant disadvantages typical of underdamped valves.
  • the damping creates smoother, quieter operation, eliminates poppet chatter, reduces vibration and generally improves the valve operation and life.
  • the quick opening feature of this valve is particularly adapted to instant response to sudden, but brief, pressure surges and shocks experienced in chamber 11.
  • spring 29 compresses slightly against flange 32 and permits a limited flow out of chamber 11 and allows poppet 23 to quickly return to the closed position as pressure in chamber 11 is relieved.
  • Such operation is distinctly advantageous over previous designs where such pressure surges created improper poppet response.
  • Prior valves, having damping characteristics similar to that exhibited by the present valve during compression of spring 30, would be so slowly responsive that the poppet would not react at all to the momentary pressure surge, resulting in excessively high pressure peaks and accompanying stress upon the pressure system.
  • the present invention provides a novel biasing means that is provided with intermediate damping staging the biasing effect.
  • the one stage is undamped and sensitive to high frequency movements while the damped stage is sensitive to lower frequency, longer duration poppet movements.
  • Such biasing more nearly matches the requirements of pressure chamber 11 and reduces poppet chatter and unwanted oscillation.
  • the present invention has been found capable of being incorporated in standard valves to replace a conventional singlespring bias, since the length of springs 29 and 30 together are approximately equivalent to the length ofa corresponding single spring. This is due to the sequential arrangement of springs 29 and 30 whereby both are compressed to provide the control member biasing force. In fact, it has been found suitable in certain valves to split an existing spring into two sections, a smaller section 29 and larger section 30 to produce the improved biasing members.
  • a valve according to the invention was designed and tested in comparison to a conventional valve identical in design save for a conventional single spring biasing means.
  • the conventional valve had excellent response characteristics to shock loading as determined by a very low peak pressure overshoot, about 2,000 p.s.i. peak pressure when adjusted to crack" or open at 1,750 p.s.i.
  • the conventional valve was underdamped and oscillated creating excessive wear and undue noise. This was reflected in the wide band of pressure variation, about 1,000 p.s.i., occurring in the high pressure chamber.
  • the improved valve incorporated helical coil springs 29 and 30, both having a wire diameter ofO. 103 inches.
  • Spring 30 had a spring rate of 772 pounds/inch and was 0.780 inches long, while spring was 0.615 inches long having a spring rate of 1,080 pounds/inch.
  • Bore 18 was nominally 0.519 inches in diameter with circular flange 32 being nominally 0.512 inches leaving an annular restricted passage 35 of 0.07 inches in width.
  • the relief valve was installed and adjusted so that 1,750 p.s.i. opening pressure force in chamber 11 was required to crack" the poppet open with a back pressure of p.s.i. being maintained in exhaust chamber 12 by an appropriate needle valve.
  • the invention has been specifically shown and described as it is incorporated in a high pressure relief valve to provide proper damping without introducing sluggishness or insensitivity to its operation.
  • the invention may be similarly utilized in other types of pressure-actuated, spring-biased valves, and accordingly, the foregoing specification is to be considered exemplary in nature and not limiting to the scope and spirit of the invention as set forth in the appendaged claims.
  • a fluid relief valve comprising:
  • a body member defining a chamber therein and having an outlet and inlet, said body adapted to be connected to a housing with said inlet being exposed to fluid at high pressure
  • biasing means in said chamber urging said poppet to a normally closed position, said biasing means being comprised of an undamped member and a damped member, said undamped member being responsive to initial application of predetennined pressure to permit limited undamped opening ofsaid poppet and said damped member being responsive to continued application of said predetennined pressure to permit further damped opening of poppet thereby substantially reducing instability of said valve.
  • first and second members of said biasing means comprise compression springs separated by a slidable partition dividing the chamber into first and second fluid chambers respectively containing said first and second biasing means, said partition adapted to restrict fluid flow from said first chamber whereby compression ofsaid first biasing means is hydraulically damped.
  • a fluid relief valve comprising:
  • a body member defining a chamber therein and having an outlet and inlet communicating with said chamber, said body adapted to be connected to a housing with said inlet being exposed to fluid at high pressure
  • an axially movable pressure-responsive poppet in said chamber having a passageway therein coaxial with said bore, said poppet in a closed position abutting against said seat and adapted to move away from said seat upon establishing predetermined high pressure at said inlet thereby placing said inlet and outlet in hydraulic communication through said passageway, and
  • biasing means extending between said body and said poppet urging said poppet to a normally closed position, said biasing means being comprised of a damped member adjacent said body member and an undamped member adjacent said poppet, said undamped member being initially responsive to initial application of predeten'nined pressure to permit movement said poppet from said seat and said damped member being responsive to continued application of predetermined pressure whereby both said members sequentially compress to permit further opening of said poppet thereby substantially reducing instability of said valve.
  • a pressure relief valve comprising:
  • a housing member defining a central chamber closed at one end and having a fluid inlet communicating with said bore and a fluid outlet communicating with said bore intermediate the inlet and said closed end,
  • a poppet member movably disposed in said bore and cooperating with a seat to control flow therethrough from the inlet to the outlet, said poppet having a surface portion arranged whereby predetermined fluid pressure associated with the inlet exerts an opening force on said poppet urging same to an open position permitting flow from the inlet to the outlet,
  • a divider plate in said bore intermediate said closed end and said poppet closely cooperating with the bore wall to define in said bore first and second fluid chambers respectively extending axially from the closed end to said plate and from said plate to said poppet, said second chamber being in open communication with said outlet, d. flow restriction means permitting restricted fluid flow from the first to the second chamber,
  • first resilient means arranged in said first chamber between the closed end and dividing plate
  • second resilient means spring in said second chamber extending between said damping plate and said poppet, said first and second resilient means exerting a biasing force on the poppet to urge same to a normally closed flowblocking position and normally cooperatively compressing upon actuation of the poppet by sufficient inlet pressure wherein poppet movement is hydraulically damped and whereby said second resilient means is capable of limited compression against said damping plate independent of first spring compression to permit undamped opening movement of said poppet.
  • damping plate includes a protuberant portion extending axially into said second chamber toward said poppet and having a conically formed end for diverting axially directed fluid flow from the inlet through said poppet central bore radially outwardly toward said outlet.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Safety Valves (AREA)
  • Control Of Fluid Pressure (AREA)
US3621875D 1969-11-25 1969-11-25 Pressure-actuated valve Expired - Lifetime US3621875A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US87981669A 1969-11-25 1969-11-25

Publications (1)

Publication Number Publication Date
US3621875A true US3621875A (en) 1971-11-23

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Family Applications (1)

Application Number Title Priority Date Filing Date
US3621875D Expired - Lifetime US3621875A (en) 1969-11-25 1969-11-25 Pressure-actuated valve

Country Status (6)

Country Link
US (1) US3621875A (fr)
JP (1) JPS4815966B1 (fr)
DE (1) DE2057363C3 (fr)
FR (1) FR2071727A5 (fr)
GB (1) GB1319802A (fr)
SE (1) SE371706B (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4275865A (en) * 1977-08-24 1981-06-30 Lucas Industries Limited Fluid control valves
US5826735A (en) * 1996-08-05 1998-10-27 Emerald Rail Technologies, Llc Railcar cushion device valving systems
US5871109A (en) * 1996-08-05 1999-02-16 Emerald Rail Technologies, Llc Railcar cushion device preload valving systems
EP1239154A2 (fr) * 2001-03-06 2002-09-11 Kabushiki Kaisha Toyota Jidoshokki Compresseur avec soupape de surpression
WO2006100603A1 (fr) * 2005-03-25 2006-09-28 O.M.T. Officina Meccanica Tartarini S.R.L. Regulateur de pression de gaz et procede d'assemblage et de demontage dudit regulateur
US20230077254A1 (en) * 2021-07-06 2023-03-09 Saudi Arabian Oil Company Preventing an over pressure condition with a mechanical shutdown valve

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5421313U (fr) * 1977-07-15 1979-02-10
FR2473670B1 (fr) * 1980-01-15 1985-06-28 Electricite De France Soupape de surete equipee d'un frein hydraulique et frein hydraulique susceptible d'etre insere dans une soupape existante
DE3204408C2 (de) * 1982-02-09 1985-10-10 Alfred Teves Gmbh, 6000 Frankfurt Verfahren zum Einstellen eines Schaltdrucks bei einer Ventilanordnung für einen Fluiddruckregler, Ventilanordnung zur Durchführung des Verfahrens und Fluiddruckregler mit zwei an jeweils einen eigenen Fluidkreis anschließbaren Ventilanordnungen
JPS5982565U (ja) * 1982-11-24 1984-06-04 今田　誠人 温室用消毒液噴霧装置
JPS60160166U (ja) * 1984-03-30 1985-10-24 モノレ−ル工業株式会社 ビニ−ルハウス用の薬液等の散布装置
DE8526293U1 (de) * 1985-09-12 1985-10-24 Joh. Vaillant Gmbh U. Co, 5630 Remscheid Strömungsregler
JPS62143616A (ja) * 1986-12-12 1987-06-26 ヤンマー農機株式会社 育苗施設
JPH01130675U (fr) * 1988-02-26 1989-09-05
JP6154672B2 (ja) 2013-06-13 2017-06-28 株式会社ダイヘン 溶接電源のくびれ検出制御方法

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US898659A (en) * 1907-08-22 1908-09-15 Theodore Kolischer Compressor.
US2518387A (en) * 1944-11-03 1950-08-08 Eaton Mfg Co Relief valve
US2686534A (en) * 1950-09-27 1954-08-17 Montelius Carl Oscar Josef Nonchattering relief valve
US3054420A (en) * 1958-10-03 1962-09-18 Commercial Shearing Relief valves
US3130748A (en) * 1961-04-17 1964-04-28 Kugelfischer G Schaefer & Co Check valve for fuel injection pumps
US3370601A (en) * 1964-01-02 1968-02-27 Ohio Brass Co Valve for controlling the rate of movement of a fluid powered motor unit

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US898659A (en) * 1907-08-22 1908-09-15 Theodore Kolischer Compressor.
US2518387A (en) * 1944-11-03 1950-08-08 Eaton Mfg Co Relief valve
US2686534A (en) * 1950-09-27 1954-08-17 Montelius Carl Oscar Josef Nonchattering relief valve
US3054420A (en) * 1958-10-03 1962-09-18 Commercial Shearing Relief valves
US3130748A (en) * 1961-04-17 1964-04-28 Kugelfischer G Schaefer & Co Check valve for fuel injection pumps
US3370601A (en) * 1964-01-02 1968-02-27 Ohio Brass Co Valve for controlling the rate of movement of a fluid powered motor unit

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4275865A (en) * 1977-08-24 1981-06-30 Lucas Industries Limited Fluid control valves
US5826735A (en) * 1996-08-05 1998-10-27 Emerald Rail Technologies, Llc Railcar cushion device valving systems
US5871109A (en) * 1996-08-05 1999-02-16 Emerald Rail Technologies, Llc Railcar cushion device preload valving systems
EP1239154A2 (fr) * 2001-03-06 2002-09-11 Kabushiki Kaisha Toyota Jidoshokki Compresseur avec soupape de surpression
EP1239154A3 (fr) * 2001-03-06 2004-02-04 Kabushiki Kaisha Toyota Jidoshokki Compresseur avec soupape de surpression
WO2006100603A1 (fr) * 2005-03-25 2006-09-28 O.M.T. Officina Meccanica Tartarini S.R.L. Regulateur de pression de gaz et procede d'assemblage et de demontage dudit regulateur
US20060219966A1 (en) * 2005-03-25 2006-10-05 O.M.T. Officina Meccanica Tartarini S.R.I Gas pressure regulator and method for assembling and disassembling the regulator
US7748401B2 (en) 2005-03-25 2010-07-06 O.M.T. Officina Meccanica Tartarini S.R.L. Gas pressure regulator and method for assembling and disassembling the regulator
US20100243080A1 (en) * 2005-03-25 2010-09-30 Fisher Controls International Llc Gas Pressure Regulator and Method for Assembling and Disassembling the Regulator
US20100243081A1 (en) * 2005-03-25 2010-09-30 Fisher Controls International Llc Gas Pressure Regulator and Method for Assembling and Disassembling the Regulator
US8267110B2 (en) 2005-03-25 2012-09-18 O.M.T. Officina Meccanica Tartarini S.R.L. Gas pressure regulator and method for assembling and disassembling the regulator
US8322359B2 (en) 2005-03-25 2012-12-04 O.M.T. Officina Meccanica Tartarini S.r.I. Gas pressure regulator and method for assembling and disassembling the regulator
US20230077254A1 (en) * 2021-07-06 2023-03-09 Saudi Arabian Oil Company Preventing an over pressure condition with a mechanical shutdown valve
US11821543B2 (en) * 2021-07-06 2023-11-21 Saudi Arabian Oil Company Preventing an over pressure condition with a mechanical shutdown valve

Also Published As

Publication number Publication date
DE2057363B2 (de) 1979-05-23
GB1319802A (en) 1973-06-13
SE371706B (fr) 1974-11-25
DE2057363C3 (de) 1980-02-07
FR2071727A5 (fr) 1971-09-17
JPS4815966B1 (fr) 1973-05-18
DE2057363A1 (de) 1971-06-09

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AS Assignment

Owner name: EATON CORPORATION, EATON CENTER, CLEVELAND, OH 441

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:CESSNA AIRCRAFT COMPANY, THE;REEL/FRAME:004991/0073

Effective date: 19880930