EP2160535A2 - Soupape de libération de pression et procédé pour composants sous-marins - Google Patents

Soupape de libération de pression et procédé pour composants sous-marins

Info

Publication number
EP2160535A2
EP2160535A2 EP08826060A EP08826060A EP2160535A2 EP 2160535 A2 EP2160535 A2 EP 2160535A2 EP 08826060 A EP08826060 A EP 08826060A EP 08826060 A EP08826060 A EP 08826060A EP 2160535 A2 EP2160535 A2 EP 2160535A2
Authority
EP
European Patent Office
Prior art keywords
relief valve
piston
seal
test
pressure
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.)
Withdrawn
Application number
EP08826060A
Other languages
German (de)
English (en)
Other versions
EP2160535A4 (fr
Inventor
Patrick Rawls
Ryan Gustafson
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.)
Hydril USA Distribution LLC
Original Assignee
Hydril USA Manufacturing LLC
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 Hydril USA Manufacturing LLC filed Critical Hydril USA Manufacturing LLC
Publication of EP2160535A2 publication Critical patent/EP2160535A2/fr
Publication of EP2160535A4 publication Critical patent/EP2160535A4/fr
Withdrawn legal-status Critical Current

Links

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
    • F16K17/0446—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 an obturating member having at least a component of their opening and closing motion not perpendicular to the closing faces
    • F16K17/046—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 an obturating member having at least a component of their opening and closing motion not perpendicular to the closing faces the valve being of the gate valve type or the sliding valve type

Definitions

  • Embodiments of the present disclosure relate to a pressure relief system for subsea vessels. More particularly, embodiments of the present disclosure relate to a relief valve for subsea vessels.
  • Pressure vessels used subsea to maintain and simulate an ambient pressure similar to what is experienced at the surface are often called "one atmosphere chambers.”
  • a common use in the oil industry for such chambers may be to protect pressure sensitive components subsea.
  • a pressure chamber leaks slowly while subsea, and then is withdrawn back to surface relatively rapidly, it may contain hyperbaric pressure, or pressure higher than normal atmospheric pressure. With depths reaching close to 10,000 ft, this pressure may become extremely large (about 0.47 psi per foot of depth), even as high as 5000 psi.
  • a large pressure buildup inside the subsea chamber may be capable of releasing large amounts of energy when retrieved and brought to the surface.
  • a relief system may be implemented to reduce the pressure inside the chamber to an acceptable and safe level as it is retrieved to the surface.
  • Pressure relief valves are commonly provided in various systems to limit the maximum pressure to less then a predefined threshold level.
  • a pressure relief valve may be provided at the outlet of a pump so that the supply line may not be pressurized to an excessive level. Should the pressure threshold level be exceeded, the relief valve opens, thereby creating a path to a reservoir, or tank.
  • Another pressure relief valve may be provided at the workport of a control valve assembly to which a hydraulic actuator, such as a piston and cylinder combination, is connected. This arrangement may protect against shock loading or inertial overloading from the load acting on the piston and cylinder. If that load results in an excessively high pressure within the hydraulic lines attached to the cylinder, the workport pressure relief valve is designed to open to relieve pressure to the system tank. The workport relief valve may remain open until the load condition no longer exists and pressure within the hydraulic line decreases below a threshold pressure.
  • One type of relief valve includes a movable element biased against a valve seat by a spring to maintain the valve in a closed state.
  • the valve element moves away from the seat, thereby opening the pressure relief valve.
  • the valve opens as soon as the spring force is exceeded and closes immediately upon the pressure dropping below the spring force.
  • the valve may be desirable for the valve not to open immediately when the pressure threshold is exceeded, but rather to delay opening until the excessive pressure exists for a given amount of time.
  • a pressure relief valve may be less affected by occasional short duration pressure events which exceed the threshold level.
  • the valve opens to relieve that pressure before damage to the hydraulic system can occur.
  • 6,957,660 assigned to Holder, discloses a pressure relief valve having a valve element that is biased by a spring into a closed position.
  • a pressure being controlled, or regulated is applied to the valve element to counter the force of the spring.
  • the pressure applied to the valve element exceeds the force of the spring the pressure relief opens.
  • the pressure applied to the valve element falls below the force of the spring, the valve closes.
  • U.S. Patent No. 3,945,395, assigned to Reinicke, et. al discloses a vent and relief valve for a tank containing pressurized fluid characterized in that coaxial vent and relief valve members have inter-engaged seats to close the vent outlet of the valve. Vent and relief valve further comprises an actuating means associated therewith to disengage said seats to open communication between the interior of the tank and the vent outlet of the valve as during filling of the tank.
  • the relief valve member is actuated by fluid pressure in the tank exceeding a predetermined value to move said relief valve member to disengage said seats and thereby again establish communication between the interior of the tank and the vent outlet of the valve thus to vent excess fluid pressure.
  • API American Petroleum Institute
  • ANSI American National Standards Institute
  • API produces standards, recommended practices, specifications, codes and technical publications, reports and studies that cover each segment of the industry. API standards promote the use of safe, interchangeable equipment and operations through the use of proven, sound engineering practices.
  • API specification 16D discusses standards for electrical and electronic chambers, a vessel on which a relief valve may be used. "All electrical and electronic chambers shall be double sealed at all areas exposed to seawater or hydrostatic pressure and should have a provision for a test port. These test ports shall be plugged and sealed when not in use for testing”. (API 16D). As such, a relief valve having a double seal between the interior volume of a vessel and an exterior subsea environment, as well as a test port, would be well received in industry. Furthermore, the ability to test both a front and backside of the seals as in a factory acceptance test would be highly desirable. Summary of Invention
  • a relief valve for a pressure vessel includes a housing having an inner bore extending between an inlet and an outlet, a piston located within the inner bore, and a spring disposed about the piston and configured to bias the piston into a closed position. Furthermore, the relief valve includes a test port in communication with the inner bore, a removable test plug sealingly disposed within the test port, and a first seal and a second seal disposed within the inner bore on either side of the test port. Preferably, the first and second seals configured to engage the piston and hydraulically isolate the inlet from the outlet when the piston is in the closed position.
  • a relief valve for a pressure vessel includes a housing comprising an inlet and an outlet, a piston located within the housing, the piston biased into a closed position by a spring, and a first seal and a second seal configured to hydraulically isolate the inlet from the outlet when the piston is in the closed position.
  • the piston configured to move out the closed position when a force exerted on the piston by fluids of the pressure vessel exceeds a force of the spring.
  • a method to test a relief valve includes applying a test pressure to a backside of a first and a second seal through a test port of the relief valve.
  • Figure 1 is a relief valve in a closed position in accordance with embodiments of the present disclosure.
  • Figure 2 is a relief valve in an open, or vent, position in accordance with embodiments of the present disclosure.
  • Figure 3 is a relief valve in a test position in accordance with embodiments of the present disclosure.
  • Figure 4 is a relief valve in a closed position in accordance with embodiments of the present disclosure.
  • Figure 5 is a relief valve in a vent position in accordance with embodiments of the present disclosure.
  • Embodiments disclosed herein relate to a relief valve for a subsea pressure vessel. More particularly, the present embodiments disclose an apparatus and method for a relief valve for a subsea pressure vessel.
  • Relief valve 100 includes a housing 102 having an inner bore 104 which allows communication between an inlet 106 and an outlet 108.
  • Relief valve 100 further comprises a piston 110 disposed in inner bore 104, a spring 112 disposed in inner bore 104 and acting upon piston 110, and a first seal 114 and a second seal 116, both of which are circumferentially disposed on and configured to dynamically seal on piston 110.
  • Relief valve 100 also includes a test port 118 in communication with inner bore 104, and a test plug 120 removeably and sealably disposed in test port 118.
  • test port 118 and test plug 120 may be replaced with a test valve without departing from the present disclosure.
  • Test plug 120 is described as being removeably disposed in test port 118, therefore, it should be understood that engagement in test port 118 could be accomplished by means such as threading, welding, brazing, epoxy, and any other fastening method known to one of ordinary skill in the art.
  • sealably refers to any method know to one of ordinary skill in the art, including, but not limited to, elastomeric seals, rubber seals, metal-to-metal seals, etc.
  • relief valve 100 is in a "closed" position, wherein spring 1 12 is uncompressed and piston 110 is in sealed engagement with first seal 114 and second seal 116.
  • relief valve 100 prevents communication of a pressure between inlet 106 and outlet 108.
  • relief valve 100 is shown in a "vent" position in accordance with embodiments of the present disclosure.
  • the vent position is described as when spring 112 is compressed and piston 110 is axially displaced within inner bore 104 and out of sealed engagement with first seal 114 and second seal 116.
  • Pressure inside a vessel is constantly applied through an inlet onto an area of an end face 122 of piston 110.
  • the force applied to end face 122 of piston 110 becomes greater than a force of spring 112 thereby causing axial displacement of piston 110.
  • piston 110 breaks contact with first seal 114 and second seal 1 16, allowing pressure to escape or "vent" through outlet 108. It should be noted that pressure may be unable to escape through relief valve 100 until piston 110 is out of sealable engagement with both first seal 114 and second seal 116.
  • the preset spring force of spring 112 is able to overcome the applied force from the vessel, and piston 110 is displaced back into sealable engagement with second seal 1 16 at which point pressure is unable to vent. Piston 110 continues to be displaced and sealably engage first seal 114, at which point spring 112 is substantially uncompressed and relief valve is once again in a closed position.
  • the spring force acting upon the piston may be provided by any means known in the art including, but not limited to, metal coiled springs, Belleville washers, elastomeric springs, etc.
  • relief valve 100 is shown in a "test" position in accordance with embodiments of the present disclosure.
  • the test position is described as when the test plug (120 of Figure 1 & 2) is removed from test port 118 and pressure is able to be applied to "backside" surfaces of first seal 1 14 and second seal 1 16.
  • Backside 130 of first seal 114 is the face of the seal facing away from inlet 106
  • backside 132 of second seal 116 is the face of the seal facing away outlet 108.
  • backside 130 of first seal 114 and backside 132 of second seal 116 face each other.
  • piston 110 maintains contact with both first seal
  • test plug (not shown) has been removed from test port 118 to allow access to "backsides" of first seal 1 14 and second seal 116 for pressure testing and a test pressure is applied through test port 1 18 and into inner bore 104.
  • the test pressure may be a working pressure of the valve to simulate working conditions, or any other appropriate pressure know to one of ordinary skill in the art.
  • First seal 114 and second seal 1 16 may be simultaneously tested to ensure proper sealing for seals between piston 110 and inner bore 104.
  • pressurization of inner bore 104 and test port 118 is discontinued and test plug (not shown) is reinstalled in test port 118.
  • test plug may be replaced with a test valve, etc. without departing from embodiments disclosed.
  • Relief valve 200 comprises a housing 202 having an inner bore 204 which allows communication between an inlet 206 and an outlet 208.
  • Relief valve 200 further comprises a piston 210 disposed within inner bore 204, a spring 212 disposed within inner bore, a first seal 214 and a second seal 216 in sealing engagement with piston 210, and a test port 218 with a test plug 220 removeably and sealably disposed within.
  • piston 210 comprises leak ports 222, which may include circumferential grooves, axial grooves, drilled holes or any other configuration known to one of ordinary skill in the art.
  • Relief valve 200 is shown in a closed position, described as when piston 210 is sealably engaged with first seal 214 and second seal 216 thereby disallowing communication of pressure between inlet 206 and outlet 208.
  • Relief valve 200 is shown in a vent position, in which piston 210 has been displaced out of sealable engagement with first seal 214 by pressure inside of a chamber. Pressure inside the chamber enter inlet 206 is applied on an area of an end face 224 of piston 210. When the pressure inside the chamber reaches a certain level, it overcomes a preset force applied to piston 210 by spring 212, and begins to compress spring 212 and move piston 210 out of sealable engagement with first seal 214. Also, a portion of the leak ports 222 is displaced past second seal 216, thereby allowing full communication of pressure between inlet 206 and outlet 208.
  • piston 210 is moved back into sealable engagement with first seal 214, and leak ports 222 are moved back into the closed position so as to disallow further communication of pressure through inner bore 204.
  • spring force acting upon the piston may be provided by any means known in the art, including, but not limited to, metal coiled springs, Belleville washers, elastomeric springs, etc.
  • relief valve 200 may be configured in such a way as to test a backside of both seals.
  • test plug 220 may be removed and a test pressure applied through test port 218 and into inner bore 204.
  • a test pressure is applied to backsides of both first seal 214 and second seal 216 with piston 210 in a closed position.
  • pressure is discontinued and test plug 220 is disposed within test port 218.
  • test plug may be replaced with a test valve, etc. without departing from embodiments disclosed.
  • alternate embodiments of the present disclosure include a relief valve comprising seals, wherein at least one of the seals may be a metal-to-metal seal.
  • the metal-to-metal seal may be the first or primary seal, while the second seal may be an elastomeric seal.
  • the metal-to-metal seal may be the second seal, while the first seal is an elastomeric seal.
  • both the first and second seals may be metal-to-metal seals.
  • embodiments using metal-to-metal seals may require a spring having a larger spring force because of the high contact stresses that may be needed to create a metal-to-metal seal.
  • alternate embodiments of the present disclosure may include a first seal area that is larger than the second seal area. Because of the larger first seal area, the valve may be able to relieve, or vent, at lower pressures.
  • Embodiments of the present disclosure advantageously allow for a backside seal test of both seals.
  • Reciprocating motion as is present between the piston and the two seals adds a extra dimension to the sealing problem.
  • Friction, and its associated wear, join a list of factors that must be contended with including temperature, fluid compatibility, and pressure.
  • the seals used for sealing a reciprocating member must meet static and dynamic sealing requirements at their contact areas with the stationary member, which is the inner bore, and also seal effectively at their contact areas on the reciprocating member, in this case the piston. To ensure reliability of a seal, it may be desirable and advantageous to be able to test both sides of a seal from opposite directions.
  • embodiments of the present disclosure preferably conform to API standard 16D, which requires a "double seal" between an inner chamber of a pressure vessel and an outer subsea environment. Since the relief valve provides communication between the two, a double seal is a desirable feature. According to API Specification 16D, chambers shall be double sealed at all areas exposed to seawater or hydrostatic pressure. Furthermore, a test port may be used, and when present should be plugged and sealed when not in use for testing. The double seal configuration of relief valve is a built-in redundancy that may be appreciated by one of ordinary skill in the art.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Safety Valves (AREA)
  • Details Of Valves (AREA)

Abstract

La présente invention concerne une soupape de libération d'une cuve sous pression qui comprend un logement ayant un alésage interne se prolongeant entre une entrée et une sortie, un piston situé dans l'alésage interne, un ressort disposé autour du piston et configuré pour dériver le piston dans une position fermée, un orifice de test en communication avec l'alésage interne, une prise de test amovible disposée de manière étanche dans l'orifice de test, ainsi qu'un premier et second joint disposés dans l'alésage interne de l'un ou l'autre côté de l'orifice de test, le premier et le second joints étant configurés pour engager le piston et isoler au plan hydraulique l'entrée de la sortie lorsque le piston est en position fermée.
EP08826060.9A 2007-05-01 2008-04-30 Soupape de libération de pression et procédé pour composants sous-marins Withdrawn EP2160535A4 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US91517007P 2007-05-01 2007-05-01
PCT/US2008/061979 WO2009005883A2 (fr) 2007-05-01 2008-04-30 Soupape de libération de pression et procédé pour composants sous-marins

Publications (2)

Publication Number Publication Date
EP2160535A2 true EP2160535A2 (fr) 2010-03-10
EP2160535A4 EP2160535A4 (fr) 2017-06-07

Family

ID=40226742

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08826060.9A Withdrawn EP2160535A4 (fr) 2007-05-01 2008-04-30 Soupape de libération de pression et procédé pour composants sous-marins

Country Status (10)

Country Link
EP (1) EP2160535A4 (fr)
CN (1) CN101675282B (fr)
AR (1) AR066413A1 (fr)
AU (1) AU2008270957B2 (fr)
BR (1) BRPI0809878A2 (fr)
CA (1) CA2685771C (fr)
MX (1) MX2009011845A (fr)
MY (1) MY154506A (fr)
SG (1) SG10201509023QA (fr)
WO (1) WO2009005883A2 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8393399B2 (en) * 2010-11-30 2013-03-12 Hydril Usa Manufacturing Llc Blowout preventer with intervention, workover control system functionality and method
CN105003701B (zh) * 2015-08-03 2017-09-22 南京理工大学 一种开启压力可变的稳压阀
DE102015220306A1 (de) * 2015-10-19 2017-04-20 Robert Bosch Gmbh Druckausgleichsvorrichtung
CN106523782A (zh) * 2016-12-23 2017-03-22 王小东 一种能用于压力检测的多功能安全阀
CN109681684B (zh) * 2019-01-21 2020-08-04 中国船舶科学研究中心（中国船舶重工集团公司第七0二研究所） 一种适用于潜水器管路系统的应急抛载安全阀
CN110761757B (zh) * 2019-11-29 2021-08-06 李杨 多管式均衡注水量高效分层注水调节装置
CN112754372B (zh) * 2020-12-28 2022-05-24 科沃斯商用机器人有限公司 一种密封结构和自移动清洁机器人

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US4314579A (en) * 1980-03-18 1982-02-09 Charles Wheatley Gate valve
US4614201A (en) * 1981-06-15 1986-09-30 King Frank E Break-away coupling for hoselines
US4548067A (en) * 1984-04-09 1985-10-22 Hydro-Seal Valve Company, Inc. Method and apparatus for testing a relief valve
DE3420890A1 (de) * 1984-06-05 1985-12-05 Gewerkschaft Eisenhütte Westfalia, 4670 Lünen Druckbegrenzungsventil, insbesondere fuer hydraulische teleskopstempel u.dgl.
DE3518472A1 (de) * 1985-05-23 1986-11-27 Jörn 4320 Hattingen Dams Druckbegrenzungsventil
CA2033066A1 (fr) * 1989-05-19 1990-11-20 Richard Voss Robinet limiteur de pression a piston etage ou double
CN2080604U (zh) * 1990-09-29 1991-07-10 李立夫 静止减压阀
DE4302080C1 (de) * 1993-01-27 1994-08-18 Vos Richard Grubenausbau Gmbh Kleinbauendes Druckbegrenzungsventil mit hoher Durchflußleistung
JPH11230352A (ja) * 1998-02-10 1999-08-27 Nec Corp 密閉容器及びその試験方法
FR2818727B1 (fr) * 2000-12-21 2004-12-17 Taema Soupape a amplification d'ouverture et regulateur de pression equipe d'une telle soupape
CN2530116Y (zh) * 2002-03-21 2003-01-08 上海航空电器厂 高压清洗机启停泄压阀
KR100430786B1 (ko) * 2002-03-22 2004-05-17 손형모 체크밸브

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Title
See references of WO2009005883A2 *

Also Published As

Publication number Publication date
CN101675282A (zh) 2010-03-17
SG10201509023QA (en) 2015-12-30
CN101675282B (zh) 2012-06-13
WO2009005883A3 (fr) 2009-07-09
CA2685771A1 (fr) 2009-01-08
CA2685771C (fr) 2015-10-20
AR066413A1 (es) 2009-08-19
EP2160535A4 (fr) 2017-06-07
AU2008270957B2 (en) 2014-04-03
BRPI0809878A2 (pt) 2014-09-30
MX2009011845A (es) 2009-11-26
AU2008270957A1 (en) 2009-01-08
WO2009005883A2 (fr) 2009-01-08
MY154506A (en) 2015-06-30

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