US20060159569A1 - Pump device for the hydraulic actuation of a valve - Google Patents

Pump device for the hydraulic actuation of a valve Download PDF

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Publication number
US20060159569A1
US20060159569A1 US10/564,584 US56458404A US2006159569A1 US 20060159569 A1 US20060159569 A1 US 20060159569A1 US 56458404 A US56458404 A US 56458404A US 2006159569 A1 US2006159569 A1 US 2006159569A1
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United States
Prior art keywords
pump device
piston
valve
hydraulic fluid
safety valve
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Abandoned
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US10/564,584
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English (en)
Inventor
Klaus Biester
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OneSubsea IP UK Ltd
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Cooper Cameron Corp
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Assigned to COOPER CAMERON CORPORATION reassignment COOPER CAMERON CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: BIESTER, KLAUS
Publication of US20060159569A1 publication Critical patent/US20060159569A1/en
Assigned to CAMERON INTERNATIONAL CORPORATION reassignment CAMERON INTERNATIONAL CORPORATION CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: COOPER CAMERON CORPORATION
Priority to US13/096,934 priority Critical patent/US8770950B2/en
Assigned to ONESUBSEA, LLC reassignment ONESUBSEA, LLC ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: CAMERON INTERNATIONAL CORPORATION
Assigned to ONESUBSEA IP UK LIMITED reassignment ONESUBSEA IP UK LIMITED ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ONESUBSEA, LLC
Assigned to ONESUBSEA IP UK LIMITED reassignment ONESUBSEA IP UK LIMITED CORRECTIVE ASSIGNMENT TO CORRECT THE PATENT NO. 8385005 PREVIOUSLY RECORDED ON REEL 035135 FRAME 0474. ASSIGNOR(S) HEREBY CONFIRMS THE CORRECT PATENT NO. IS 8638005. Assignors: ONESUBSEA, LLC
Assigned to ONESUBSEA, LLC reassignment ONESUBSEA, LLC CORRECTIVE ASSIGNMENT TO CORRECT THE INCORRECT PATENT NO. 8385005 PREVIOUSLY RECORDED AT REEL: 035134 FRAME: 0239. ASSIGNOR(S) HEREBY CONFIRMS THE ASSIGNMENT. Assignors: CAMERON INTERNATIONAL CORPORATION
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • 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
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid

Definitions

  • the invention relates to a pump device for the hydraulic actuation of a valve, especially employed in the production of crude oil or natural gas, as a safety valve assigned to a pipeline or to a tree, with a piston-cylinder unit from which hydraulic fluid can be pumped under pressure in the direction of the valve.
  • Corresponding pump devices are known from practice, which are generally arranged far away from the actual valve and do not just supply it with hydraulic fluid, but also other equipment, in particular for crude oil or natural gas production.
  • the appropriate valve is in this respect assigned to a pipeline or similar facility as a safety valve and is generally termed a downhole safety valve.
  • a safety valve In marine crude oil or natural gas production it is arranged along the pipeline and below the surface of the sea and is used for closing the pipeline in the case, for example, of a leak or similar problem.
  • the object of the invention is to improve a pump device of the type mentioned at the beginning such that the hydraulic fluid pressure, in particular at the point of application and in the vicinity of the actual valve, can be constructively simply produced in a safe and controlled manner.
  • an electrical drive device is used which is movably connected to the appropriate piston of the piston-cylinder unit for its alternating movement in the piston longitudinal direction within the associated cylinder.
  • an electrically driven pump device pumping hydraulic fluid is provided which can specifically feed hydraulic fluid to a safety valve, whereby the corresponding pressure of the hydraulic fluid can be set and monitored by means of the electrical drive device.
  • the electrical drive device in this respect exhibits sufficient power to generate adequate hydraulic pressure for the valve.
  • the drive device can be actuated and its activity monitored by means of appropriate electrical connecting lines.
  • an electrical drive device can be used which exhibits a spindle drive, a reduction gear, a spur gear and at least one drive shaft with at least one electric motor to turn it.
  • an electrical drive device is produced which operates extremely free of maintenance and can be controlled and regulated accurately and can also be used for many other devices in the production or mining of crude oil and natural gas.
  • the rotational speed of the electric motor is reduced by the reduction gear, spur gear and also the spindle drive so far that also slight piston displacements are possible. Consequently the hydraulic pressure or the quantity of the hydraulic fluid, which is pumped through the pump device in the direction of the valve, can be set extremely precisely.
  • the spindle drive can exhibit a rotatable, but axially immovable spindle nut and an axially movable threaded spindle.
  • the corresponding axial movement of the threaded spindle can be converted into a movement of the piston in the piston longitudinal direction.
  • the threaded spindle can be releasably joined at its actuating end to the piston. In this way other intermediate components can be omitted, whereby the construction of the pump device is extremely compact.
  • a low-wear and heavy duty reduction gear which also contributes to the compactness of the pump device according to the invention, can be seen in that the spindle nut is movably connected to the reduction gear, which is in particular formed as a so-called harmonic drive gear.
  • the spindle nut is rotationally rigidly joined to a flexible, cup-shaped toothed sleeve of the harmonic drive gear.
  • This connection can occur directly or through the intermediate placement of another component.
  • a rotating sleeve can be arranged between the toothed sleeve and the spindle nut, the rotating sleeve being rotationally rigidly connected at one end to the toothed sleeve and at the other end to the spindle nut.
  • This rotating sleeve is for example supported rotationally by means of oblique roller bearings inside the pump device.
  • a harmonic drive gear Apart from the toothed sleeve, a harmonic drive gear generally exhibits a wave generator and a rotationally rigid ring element.
  • the wave generator is arranged inside the toothed sleeve and deflects it so far radially outwards at two opposite points due to its flexibility that outer teeth on the toothed sleeve engage inner teeth on the fixed ring element at these two opposite points.
  • the wave generator of the harmonic drive gear can be rotationally rigidly joined to a first spur wheel of the spur gear, whereby a second spur wheel is arranged rotationally rigidly on the drive shaft which is driven by at least one motor.
  • This type of spur gear is also extremely low-wearing, is characterised by a high efficiency and can, where applicable, be formed to be self-locking and self-braking.
  • One possibility for this type of spur gear is a double helical gear.
  • two or more electric motors can transfer their driving power to it or that two or more drive shafts can be arranged in the circumferential direction about the first spur wheel of the spur gear with corresponding electric motors. Consequently, appropriate redundancy of the drive is provided, whereby due to the many electric motors driving a drive shaft, also smaller and more economical motors can be used which through combined action produce a correspondingly high and desired drive power.
  • Simple suction of hydraulic fluid and pumping in the direction of the valve can for example be realised in that the piston is supported for adjustment in a piston chamber of the cylinder in the piston longitudinal direction, whereby the piston chamber exhibits at least a suction and a discharge opening on its face side.
  • the hydraulic fluid can be drawn into the piston chamber via the suction hole with appropriate movement of the piston and on changing the direction of piston movement, the drawn-in hydraulic fluid can be pumped under pressure in the direction of the valve via the discharge hole.
  • a non-return valve In order to close the respective other hole during suction and pumping in a simple manner, a non-return valve, subject to a force and set opposing the hydraulic fluid flow direction through this hole, can be assigned to each hole. This means that with the suction hole the non-return valve is subject to a force in the direction of the suction hole and in the direction of the piston for the discharge hole. Each respective non-return valve only opens through the corresponding piston movement in order to open the suction hole or alternatively the discharge hole.
  • the holes can be formed in a cylinder bottom plate, in particular releasably fixed, on the cylinder.
  • the holes pass through this cylinder bottom plate, whereby the corresponding non-return valves are assigned to the holes in the piston chamber.
  • the end of the suction hole facing away from the piston opens into an intermediate reservoir of the pump device.
  • this intermediate reservoir there is at least so much hydraulic fluid that the operation is ensured for a certain time even with an interruption in the further feed of the hydraulic fluid.
  • the intermediate reservoir can also be used for other purposes, as will be explained in the following.
  • the discharge opening can be joined to a discharge pipe for carrying the hydraulic fluid in the direction of the valve.
  • the discharge pipe can be brought out through the intermediate reservoir from a pump housing.
  • a connecting pipe for the connection of an accumulator can branch off the discharge pipe.
  • This accumulator contains sufficient hydraulic fluid to be able to compensate leakage losses over a longer time period and it also stores hydraulic fluid so that the pump device is only used intermittently.
  • the accumulator exhibits a pressure storage device, especially in the form of Belleville springs.
  • Belleville springs are generally designed with a conical cup shape and are spring washers that can be loaded in the axial direction.
  • a spring assembly can be formed from these springs, whereby stacking can occur both in parallel as well as in series. Mixed types of this stacking are also possible. In this respect parallel stacking is taken to mean a similar arrangement of many springs one above the other, whereas with serial stacking springs are arranged turned through 180° relative to one another.
  • At least one branch pipe can branch off the discharge pipe and/or the discharge hole.
  • a first possibility of supplying a further device can be seen in that a first branch pipe leads to a pressure switch. This can be used such that on reaching a predetermined pressure or with the undercutting of a predetermined pressure a certain activity, signal or similar action is triggered.
  • the pressure switch outputs an electrical control signal for opening a safety valve on reaching a predetermined hydraulic fluid pressure in the first branch pipe.
  • the hydraulic fluid can where applicable be discharged from the pump device by means of the safety valve.
  • a suitable safety valve can be arranged at an appropriate point on the pump device to discharge hydraulic fluid there.
  • a possible embodiment for such a safety valve is for example a solenoid valve or similar device.
  • the safety valve can be arranged in a second branch pipe. In this way it can be subjected directly to the hydraulic fluid present from the discharge pipe and/or the discharge hole.
  • the safety valve can be formed as a mechanically actuated non-return valve. In this way the valve is simply constructed and can be always actuated reliably and under control.
  • the electrical control signal from the pressure switch can be transferred to an electric servomotor, especially a stepper motor, through which the safety valve can be mechanically actuated.
  • a pinion can be rotationally connected to the servomotor, the said pinion being drive-connected to a cam disc, whereby an actuating plunger of the safety valve is in contact with the cam disc. With appropriate rotation of the cam disc the actuating plunger of the safety valve is displaced for opening and closing the valve.
  • the cam disc exhibits at least one actuating cam along its circumference.
  • the cam disc is rotated so far by the servomotor that the cam deflects the actuating plunger, thus opening the safety valve. If a corresponding emergency is no longer present, the cam disc can be rotated back into its initial position in which the actuating cam is no longer in contact with the actuating plunger.
  • the actuating plunger can be a roller plunger which is in rolling contact with its roller on the circumferential surface of the cam disc on which the actuating cam is arranged.
  • the roller plunger can be subjected to spring pressure in the direction of the cam disc.
  • an automatic reverse rotation device can be arranged on the cam disc and/or on the servomotor for the reverse rotation of the cam disc.
  • This reverse rotation device ensures that for example with an interruption in the electrical supply, damage to the servomotor or similar problem, the safety valve can be closed again in that the cam disc is rotated back far enough whereby the actuating cam and actuating plunger are no longer in contact with one another.
  • Such a reverse rotation device can for example be directly assigned to the cam disc in that it stresses an appropriate spring during its rotation into the actuation position and can be automatically rotated back to its initial position by the spring tension where applicable.
  • a wound or spiral spring similar to a clockwork spring, can be assigned to the servomotor as a restoring device, which by means of the actuation of the servomotor for opening the safety valve can be transferred from its essentially unstressed state into a stressed state. If the servomotor operates properly, then with the reverse rotation of the cam disc the appropriate spring is reset to its essentially unstressed state. However, if the servomotor fails or can no longer be actuated, automatic restoration of the cam disc for closure of the safety valve can occur by means of the spring tension.
  • a feedback pipe for feeding back the hydraulic fluid when the safety valve opens can run from the valve to the intermediate reservoir.
  • the appropriate hydraulic fluid can also enter where applicable via the feed line opening out in the intermediate reservoir for eliminating the overpressure.
  • the amount of this hydraulic fluid to be fed back is extremely low and would only lead to a slight forcing back of the hydraulic fluid present in the feed line.
  • One module can for example comprise the electrical drive device, whereas another module includes the pump-cylinder unit and another module for example the intermediate reservoir.
  • the modules are releasably joined together and may be composed of further submodule units.
  • the cam disc can be supported rotationally on an external circumference of the rotating sleeve.
  • the spindle nut is releasably mounted, whereby the spindle nut can be arranged completely in an appropriate inner space of the rotating sleeve and whereby the cam disc can be rotationally supported at the same time in the region of this inner space on the outer circumference of the rotating sleeve.
  • a quick-release coupling device can be arranged between the pump housing and the hydraulic fluid supply pipe. If the accumulator is also mounted on the pump housing or integrated into the housing, then it can also be mounted on the appropriate feed pipe to the valve, whereby however the accumulator can also be fitted separately and by means of an appropriate dedicated quick-release coupling device to this pipe leading to the valve. In this way, there is for example the possibility of removing and replacing the pump housing with the drive device and piston-cylinder unit separately from the accumulator.
  • each of these servomotors can be separately controlled by means of an appropriate signal from the pressure switch or also by means of an external signal, whereby the safety valve is to be opened or closed.
  • various fluids can be used as the hydraulic fluid, whereby fluids already in use at the point of application can be used to advantage.
  • a fluid is for example a so-called inhibitor, which is an injection fluid for injecting into the produced material, with most trees or similar equipment in the production of crude oil and natural gas.
  • This injection fluid is adequately available in the region of a tree so that no supply problems occur at the point of application.
  • a leak of the injection fluid in the direction of the transported raw material is relatively uncritical because it is in any case added to the raw material during production.
  • a position sensor can be assigned at least to the threaded spindle.
  • the direct position of the piston is given and by means of its movement, information about the quantity of pumped hydraulic fluid is given.
  • FIG. 1 a longitudinal section through an embodiment of a pump device according to the invention
  • FIG. 2 an enlarged illustration of detail “X” from FIG. 1 .
  • FIG. 3 a section along the line III-III from FIG. 1 , whereby the longitudinal section according to FIG. 1 corresponds to a section along the line I-I from FIG. 3 .
  • FIG. 1 a longitudinal section is shown through an embodiment of a pump device 1 according to the invention.
  • This exhibits a drive device 5 , which is actuated electrically and is formed from a series of subgroups.
  • a first subgroup is a spindle drive 6 of a rotationally but axially immovably supported spindle nut 10 and an axially movable but rotationally rigidly supported threaded spindle 11 .
  • the spindle nut 10 is inserted into a corresponding inner hole or inner space of a rotating sleeve 15 and is releasably attached to it there by means of appropriate threaded bolts.
  • the rotating sleeve 15 is supported rotationally by means of a series of oblique roller bearings inside a pump housing 35 .
  • the rotating sleeve 15 is movably connected at its end facing away from the spindle nut 10 to a reduction gear 7 .
  • This reduction gear 7 as a further part of the drive device 5 is formed as a so-called harmonic drive 13 .
  • Such a harmonic drive 13 comprises a flexible toothed sleeve 14 , a fixed ring element 69 and a wave generator 18 arranged inside the toothed sleeve 14 .
  • the toothed sleeve 15 is releasably connected at its closed side to an end 16 of the rotating sleeve 15 .
  • the wave generator 18 is movably connected to a spur gear 8 as a further part of the drive device 5 .
  • a rotationally rigid connection between the wave generator 18 and a first spur wheel 19 occurs.
  • This engages at least a second spur wheel 20 whereby both spur wheels 19 , 20 form a helical gear 8 and in particular a double helical gear 22 .
  • the second spur wheel 20 is rotationally rigidly arranged at a drive shaft 21 , whereby two electric motors 9 , in particular in the form of a synchronous or asynchronous motor, act on the drive shaft 21 .
  • each of the drive shafts 21 is assigned one, two or more electric motors 9 .
  • a code carrier 69 of a position sensor 60 is inserted into it at its end assigned to the spindle nut 10 and releasably attached there.
  • Such a code carrier exhibits a position-specific pattern which is scanned by appropriate scanning devices of the position sensor 60 and converted into a corresponding position of the threaded spindle 11 .
  • the threaded spindle 11 is releasably joined at its actuating end 12 to a piston 61 which is supported for alternating movement in a corresponding piston chamber 23 of a piston-cylinder unit 3 in the longitudinal direction 24 or piston longitudinal direction 62 .
  • the piston-cylinder unit 3 comprises accordingly another cylinder 63 which is formed by various module units of the modular constructed pump housing 35 .
  • the cylinder comprises at least the housing parts in which the corresponding piston chamber 23 is contained.
  • the cylinder 63 or the piston chamber 23 exhibits a cylinder bottom plate 30 , in which a suction hole 26 and a discharge hole 27 are formed essentially parallel to one another.
  • the suction hole 26 is assigned a non-return valve 28 on the side of the piston chamber 23 , the non-return valve being subjected to spring pressure in the direction of the suction hole 26 .
  • the discharge hole 27 is assigned a non-return valve 29 on the side of the piston chamber 23 , the non-return valve being subjected to a spring pressure in the direction of the piston 61 .
  • the non-return valve 28 is opened by means of an appropriate low pressure in the piston chamber 23 and hydraulic fluid 4 enters the piston chamber 23 through the suction hole 26 . If the piston 61 moves to the right in FIG. 1 , the hydraulic fluid present in the piston chamber 23 is forced into the discharge hole 27 via the open non-return valve 29 .
  • the suction hole 26 opens with its end 32 facing away from the piston 61 into an intermediate reservoir 31 , which essentially encloses the cylinder bottom plate 30 .
  • the intermediate reservoir 31 is used for the storage of hydraulic fluid, which can be fed by means of a feed pipe 33 opening into the intermediate reservoir.
  • the feed pipe 33 is connected to a hydraulic fluid supply pipe 58 by means of a quick-release coupling device 57 .
  • This quick-release coupling device 57 is also used for the connection of a discharge pipe 34 , extending from the discharge hole 27 through the intermediate reservoir 31 and which is then routed further in the direction of the valve 2 .
  • at least the pump housing 35 of the pump device 1 is releasably attached to an appropriate device for the production of crude oil and natural gas, such as a pipeline, tree or similar facility, by the quick-release coupling device 57 .
  • the discharge pipe 34 exhibits at its section running between the quick-release coupling device 57 and the valve 2 at least a branching connecting pipe 36 , to which an accumulator 37 is connected as a pressure vessel for hydraulic fluid.
  • this pressure vessel contains a number of Belleville springs which are stacked in parallel and/or in series.
  • a first and a second branch pipe 39 , 40 branch from the discharge pipe 34 respectively from the discharge hole 27 .
  • the first branch pipe 39 extends up to a pressure switch 41 .
  • a pressure switch 41 By means of this pressure switch an electrical signal is given depending on the pressure of the hydraulic fluid in the first branch pipe 39 , at least when the hydraulic fluid exceeds a predetermined value.
  • This electrical signal is passed to a servomotor 44 , such as for example a stepper motor, for its actuation.
  • a servomotor 44 such as for example a stepper motor, for its actuation.
  • the servomotor 44 exhibits a drive shaft at one end of which a pinion 45 is arranged.
  • cam disc 46 This engages a cam disc 46 which is rotationally supported on an outer circumference 56 of the rotating sleeve 50 by means of a roller bearing 65 .
  • the cam disc 46 exhibits teeth assigned to the pinion 45 and at least an actuating cam 48 , which, with appropriate actuation of the servomotor 44 due to the electrical signal of the pressure switch 41 , comes into contact with an actuating plunger 47 , formed as a roller plunger 49 , of the safety valve 42 .
  • the roller plunger 49 exhibits on its side facing the circumferential surface 51 of the cam disc 46 a rotationally supported roller 50 .
  • the roller plunger 49 is subject to spring pressure in the direction of the circumferential surface 51 of the cam disc 46 so that the roller 50 is in rolling contact.
  • the safety valve 42 is formed as a mechanically actuated non-return valve 43 .
  • An appropriate, essentially spherical valve element can be removed from its valve seating by the actuating plunger 47 when the roller 5 runs onto the actuating cam 48 .
  • the second branch pipe 40 which is routed round the pump housing 35 up to the non-return valve 43 , is connected to a feedback pipe 55 . This opens into the intermediate reservoir 31 .
  • valve element of the non-return valve 43 is subject to a force from an appropriate spring element in the direction of the closed position so that without deflection by the actuating plunger 47 it is in the closed state.
  • a reverse rotation device 52 in the form of a wound or spiral spring 53 is assigned to the servomotor 44 on its rear side 54 facing away from the pinion 45 .
  • the wound/spiral spring is transferred from its essentially unstressed state to a stressed state. If a reverse rotation of the cam disc 46 occurs by means of the servomotor 44 for the closure of the non-return valve 43 , the wound/spiral spring is again relieved by this appropriate reverse rotation.
  • the housing 35 is overall of modular construction, whereby a first module is assigned essentially to the drive device 5 , a second module comprising where applicable submodules is assigned to the cylinder 63 and finally a module is assigned to the safety valve 42 .
  • FIG. 2 detail “X” from FIG. 1 is enlarged for the illustration of the quick-release coupling device 57 .
  • This is formed from two coupling parts 66 , 67 , which can be connected together in a simple manner for attaching the pump device to an appropriate device as well as for making the fluid connection both between the pump device 1 and valve 2 and also between the pump device 1 and hydraulic fluid supply pipe 58 .
  • the connection can be made remotely by means of appropriate vehicles.
  • FIG. 3 a section along the line III-III from FIG. 1 is illustrated, whereby FIG. 1 corresponds to a section along the line I-I in FIG. 3 .
  • an electrically actuated and operating drive device 5 is given, which is releasably attached as a module to a pump housing 35 and which acts as actuator for the actual pump of piston 61 and cylinder 63 .
  • the drive device is composed of various subgroups which operate with very low wear and are therefore maintenance-friendly and which exhibit high efficiency and a compact construction.
  • the pump device 1 is assigned a servo or stepper motor 44 which mechanically opens a safety valve 42 when the pressure is too high or a similar condition arises.
  • the servomotor 44 is arranged doubled up and each of the servomotors is assigned an automatically operating reverse rotation device 52 .
  • the hydraulic fluid used by the pump device 1 according to the invention is an injection fluid which for example is almost always used with marine trees in the production of crude oil and gas and is a so-called inhibitor. This fluid is available in adequate quantities at the point of application so that no supply deficiencies occur nor need the fluid be brought in a complex way to the appropriate point of application. Even with a leakage of the appropriate fluid there is no disadvantage, because this fluid is in any case added to the produced raw material.
  • the pump device 1 exhibits the intermediate reservoir 31 which both encloses the actual pump parts and at the same time contains a supply of the hydraulic fluid, facilitating appropriate supply with hydraulic fluid over a longer period of time if a leak occurs on the valve 2 to be supplied.
  • the feedback pipe 55 which feeds back hydraulic fluid when the safety valve trips, is also connected to this intermediate reservoir 31 . In this way there is no discharge into the environment and similarly there is no corresponding contamination nor any feedback to a remotely situated place, such as for example from the sea bed to the sea surface.
  • the accumulator 37 fulfils another important function, because it essentially acts as a pressure vessel due to the arrangement of the Belleville springs.
  • the pump can operate free of maintenance over a long period of time, whereby due to the arrangement of the pressure vessel, the pump only needs to be operated rarely.
  • the pressure vessel 37 contains hydraulic fluid with approximately 1.4 kbar. This means that the pump of the pump device 1 does not for example need to be actuated until the pressure loss in the pressure vessel amounts to less than approximately 0.4 kbar. It is only when the pressure falls below a figure of 1.0 kbar that the pump operates again and recharges the pressure vessel.
  • the complete pump device 1 can be fitted or removed in a simple manner by a remotely controlled vehicle or even by a diver at the point of application particularly also by using the quick-release coupling device 57 .
  • Appropriate monitoring of the valve 2 can also occur by means of the pump device 1 .
  • pressure monitoring or also monitoring of other features of the safety valve 2 can occur by means of the pump device 1 and its electrical connection to a remote place.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
US10/564,584 2003-07-17 2004-07-16 Pump device for the hydraulic actuation of a valve Abandoned US20060159569A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US13/096,934 US8770950B2 (en) 2003-07-17 2011-04-28 Pump device for the hydraulic actuation of a valve

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE20311033U DE20311033U1 (de) 2003-07-17 2003-07-17 Pumpvorrichtung
EP20311033.1 2003-07-17
PCT/EP2004/007948 WO2005015019A1 (en) 2003-07-17 2004-07-16 Pump device for the hydraulic actuation of a valve

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PCT/EP2004/007948 A-371-Of-International WO2005015019A1 (en) 2003-07-17 2004-07-16 Pump device for the hydraulic actuation of a valve

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US13/096,934 Continuation US8770950B2 (en) 2003-07-17 2011-04-28 Pump device for the hydraulic actuation of a valve

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US20060159569A1 true US20060159569A1 (en) 2006-07-20

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US10/564,584 Abandoned US20060159569A1 (en) 2003-07-17 2004-07-16 Pump device for the hydraulic actuation of a valve
US13/096,934 Expired - Fee Related US8770950B2 (en) 2003-07-17 2011-04-28 Pump device for the hydraulic actuation of a valve

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US (2) US20060159569A1 (pt)
BR (1) BRPI0412660A (pt)
DE (1) DE20311033U1 (pt)
GB (1) GB2419645B (pt)
NO (1) NO20060115L (pt)
WO (1) WO2005015019A1 (pt)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012018730A2 (en) * 2010-08-04 2012-02-09 Safoco, Inc. Safety valve control system and method of use
US8763983B2 (en) 2010-03-31 2014-07-01 Safoco, Inc. Safety valve and method of use
US8851108B2 (en) 2010-03-31 2014-10-07 Safoco, Inc. Safety valve and method of use
US9103465B2 (en) 2011-07-18 2015-08-11 Safoco, Inc. Dual piston actuator and method of use
US9163619B2 (en) 2010-09-17 2015-10-20 Safoco, Inc. Valve actuator control system and method of use
US9441453B2 (en) 2010-08-04 2016-09-13 Safoco, Inc. Safety valve control system and method of use
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GB2419645B (en) 2008-07-02
US20110200457A1 (en) 2011-08-18
NO20060115L (no) 2006-02-17
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US8770950B2 (en) 2014-07-08
WO2005015019A1 (en) 2005-02-17

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