WO2007043889A1 - Appareil et procédé de commande de l’alimentation en gaz barrière dans un module de compresseur - Google Patents

Appareil et procédé de commande de l’alimentation en gaz barrière dans un module de compresseur Download PDF

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Publication number
WO2007043889A1
WO2007043889A1 PCT/NO2006/000341 NO2006000341W WO2007043889A1 WO 2007043889 A1 WO2007043889 A1 WO 2007043889A1 NO 2006000341 W NO2006000341 W NO 2006000341W WO 2007043889 A1 WO2007043889 A1 WO 2007043889A1
Authority
WO
WIPO (PCT)
Prior art keywords
compartment
barrier gas
compressor
pressure
supply
Prior art date
Application number
PCT/NO2006/000341
Other languages
English (en)
Inventor
Kjell Olav Stinessen
Håkon SKOFTELAND
Audun Grynning
Original Assignee
Aker Kvaerner Subsea As
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
Priority to US12/089,413 priority Critical patent/US20080260539A1/en
Application filed by Aker Kvaerner Subsea As filed Critical Aker Kvaerner Subsea As
Priority to BRPI0616912-0A priority patent/BRPI0616912A2/pt
Priority to CA002624785A priority patent/CA2624785A1/fr
Priority to GB0805821A priority patent/GB2444220B/en
Publication of WO2007043889A1 publication Critical patent/WO2007043889A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D25/0686—Units comprising pumps and their driving means the pump being electrically driven specially adapted for submerged use
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B43/00—Methods or apparatus for obtaining oil, gas, water, soluble or meltable materials or a slurry of minerals from wells
    • E21B43/12—Methods or apparatus for controlling the flow of the obtained fluid to or in wells
    • E21B43/121—Lifting well fluids
    • E21B43/122—Gas lift
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/102—Shaft sealings especially adapted for elastic fluid pumps
    • F04D29/104—Shaft sealings especially adapted for elastic fluid pumps the sealing fluid being other than the working fluid or being the working fluid treated
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means
    • F16C32/0406—Magnetic bearings
    • F16C32/044—Active magnetic bearings
    • F16C32/047—Details of housings; Mounting of active magnetic bearings
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C39/00—Relieving load on bearings
    • F16C39/06—Relieving load on bearings using magnetic 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
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/40—Sealings between relatively-moving surfaces by means of fluid
    • F16J15/406—Sealings between relatively-moving surfaces by means of fluid by at least one pump
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/44—Centrifugal pumps

Definitions

  • the invention relates to compressor modules for compressing hydrocarbon gases in a wellstream, and more specifically it relates to a compressor module comprising a pressure housing, a compressor and a motor separated by a sealing element, as disclosed in more detail in the preamble of independent claims 1, 2 and 8.
  • the invention is especially suitable for use in subsea compressor modules.
  • a compressor module is, in its most basic form, a unit in which a compressor and a motor are connected via a shaft and placed in a common pressure shell. Between the motor and the compressor there is a seal to prevent contamination of the motor.
  • an apparatus for controlling the supply of barrier gas to a compressor module comprising a pressure housing containing an electric motor which via a shaft is drivably connected to a compressor, wherein the shaft is supported by magnetic bearings and an axial seal around the shaft divides the pressure housing into a first compartment comprising the motor and a second compartment comprising the compressor, the second compartment comprising an inlet and an outlet for fluid that is to be compressed, characterised by a line fluid-connected to the first compartment for supply of barrier gas from a reservoir, and a flow restriction means in the line between the reservoir and the first compartment.
  • an apparatus for controlling the supply of barrier gas to a compressor module comprising a pressure housing containing an electric motor which via a shaft is drivably connected to a compressor, wherein the shaft is supported by first magnetic bearings and at least one second magnetic bearing on the opposite side of the compressor in relation to the first magnetic bearings, and an axial seal around said shaft divides the pressure housing into a first compartment comprising the motor and a second compartment comprising the compressor, the second compartment comprising an inlet and an outlet for fluid that is to be compressed, and wherein a second axial seal is fitted around the shaft between the compressor and the said second magnetic bearing thereby forming a third compartment, characterised by a line fluid-connected to the first compartment and a line fluid-connected to the third compartment, the lines being arranged for supply of barrier gas from a reservoir, and respective flow restriction means in the lines between the reservoir and the first and the third compartment respectively.
  • a method for controlling the supply of barrier gas to a compressor module, characterised by, on the basis of required barrier gas velocity through the seal and the pressure in the second compartment, setting an overpressure in the reservoir, and effecting a controlled supply of barrier gas to at least the first compartment by means of the flow restriction in the feed pipe.
  • Figure 1 is a schematic diagram of the apparatus according to the invention.
  • Figure 2 is a schematic diagram of one embodiment of the barrier gas control device.
  • Figure 3 is a schematic diagram of an alternative embodiment of the barrier gas control device.
  • Figure 4 is a schematic diagram showing the gas velocity and the mass transport through the axial seal.
  • Figure 5 illustrates the barrier gas control device in a basic form.
  • Figure 6 illustrates a mechanical barrier gas control device that keeps the mass flow constant when the pressure upstream of the controller, p a , is constant and the temperature is constant, as the temperature will be when the controller is surrounded by seawater.
  • the compressor module comprises an electric motor 1 and a compressor 2, joined together via a shaft 8 and arranged in a common pressure shell 3.
  • Figure 1 illustrates schematically that a stream of essentially hydrocarbon gas, but which may also contain liquids and particles (hereafter referred to as fluid) is conducted from a reservoir (not shown), preferably via a liquid separator and in a line 17, into the compressor module via an inlet 4.
  • a reservoir not shown
  • the fluid On the upstream side (inlet side) of the compressor 2, the fluid has a suction pressure designated p s , which in a wellstream compression system will fall slowly over time as the reservoir pressure falls.
  • the fluid On the downstream side of the compressor, the fluid has a discharge pressure designated pa.
  • P d is greater than p s .
  • the pressure inside the compressor module compartments will equalise and become identical.
  • the bypass valve 61 is closed, the pressure upstream 51 may build up to become greater than the pressure downstream 61.
  • the pressure upstream 51 and downstream 61 will be equal to the settle-out pressure.
  • the pressure in the transport pipe past the compressor module may build up to WSHP.
  • the pressure inside the compressor module may therefore, due to leakage in either valve 51 or 61 or both, build up to WSHP.
  • An axial seal 31 is arranged between the compressor 2 and the motor 1 and divides the pressure shell into a first compartment 10 and a second compartment 20.
  • the purpose of the axial seal 31 is to prevent particles, moisture and other contamination from coming into contact with the motor and other electrical equipment.
  • the axial seal is not completely tight, hi the pursuit for a maximally dry and clean atmosphere in the first compartment 10, it is essential that the pressure in the first compartment 10 (where the motor is located) is higher than the pressure in the second compartment 20 (where the compressor is located) i.e., that inert gas flows from compartment 10 through the seal and into 20.
  • Figure 1 indicates this by showing that the pressure in the first compartment 10 (and in the optional third compartment, due to the balance piston) is p s + ⁇ p.
  • the shaft 8 is journalled by magnetic bearings 11, 21 as shown in Figure 1. If the magnetic bearing 21 is of the encapsulated type as described above, the axial seal 32 is superfluous. The axial seal 32 is thus optional if the magnetic bearing is encapsulated.
  • Figure 1 shows a feed line 7 for gas, connected at one end thereof to the first compartment 10 and at the other end to a gas reservoir 6 which contains gas at a pressure p a and a temperature T a .
  • the gas reservoir 6 may (optionally) be fluid- connected to another supply via a supply line 9, e.g. in a so-called umbilical.
  • gas may be delivered to the first compartment 10 from the reservoir 6.
  • This gas will be a dry hydrocarbon gas or a dry inert gas 8 (extraneous gas) which is also clean of particles.
  • This gas may come from a separate gas supply or dried hydrocarbon gas may be used.
  • the gas supplied to the compressor module via the line 7 (and the line 7', which will be described below) will hereafter be referred to as "barrier gas”.
  • the barrier gas supplied should have as low a molecular weight as possible, and thus as low a density as possible at a given pressure and temperature, because the friction decreases with decreasing gas density.
  • methane CH 4 : molecular weight 16
  • nitrogen N 2 : molecular weight 28
  • Hydrogen H 2 : molecular weight 2
  • the density of hydrogen will be about onlyl0% of a typical natural gas mixture (molecular weight 20). The density of hydrogen at 100 bars will therefore only correspond to the density of natural gas at 20 bars, with corresponding reduction of the friction loss in the motor, cooler requirement and increased efficiency of the motor.
  • the compressor's DE magnetic bearings may be located in a clutch case between the motor and the compressor, and the seal will in that case be between the clutch case and the compressor.
  • the clutch case and the motor nevertheless form an essentially common compartment with a common, clean atmosphere filled by the barrier gas.
  • the magnetic bearings are of the encapsulated type, and the operating conditions and/or the composition of the wellstream gas (the fluid) are such that these bearings can be allowed to operate directly in the wellstream gas, it is only the motor that requires protection, and the compressor's DE magnetic bearings can therefore be located on the compressor side of the seal.
  • an optional axial seal 32 may divide the second compartment 20 into a further, third compartment 30 in which the compressor module's NDE magnetic bearings maybe located.
  • An optional line 7' or 7" for the supply of barrier gas from the reservoir 6 to this third compartment is shown in Figure 1. If the magnetic bearings are of the encapsulated type, and the operating conditions and/or the composition of the wellstream gas (the fluid) are such that these bearings can be allowed to operate directly in the fluid, it is only the motor that requires protection, hi this case the seal 32 is optional.
  • the linear velocity of the barrier gas through the axial seals must be greater than or equal to and oppositely directed from the velocity of the fluid (and particles therein) in the second compartment 20.
  • gaseous contaminants in the fluid H 2 S, CO 2 , water vapour and hydrocarbon vapour molecules
  • gaseous contaminants in the fluid H 2 S, CO 2 , water vapour and hydrocarbon vapour molecules
  • An extremely small supply (mass flow per time unit) of barrier gas into the seal will therefore be sufficient to keep these contaminants out of the "clean" compartments, e.g., the first and the third compartment.
  • a critical case will be possible ingress of particles and possibly droplets that fall from the wellstream towards the seal 32 (for NDE magnetic bearings), e.g., if the compressor module is arranged vertically. Such particles may have a vertical velocity of fall in excess of 0.1 m/s.
  • Figure 4 illustrates how a minimum required barrier gas velocity through an axial seal to prevent particles from falling down through a vertically arranged seal can be calculated.
  • the barrier gas flow (m) is illustrated in Figures 1 and 4.
  • the velocity of fall is calculated using Stoke 's law:
  • V p [D p 2 (p p - p)g]/18 ⁇
  • V p velocity of fall for a particle into the seal
  • m/s V g barrier gas velocity through the seal
  • m/s D p particle diameter
  • m p p particle density
  • kg/m 3 p gas density
  • kg/m 3 g acceleration of gravity
  • m/s 2 ⁇ dynamic viscosity
  • barrier gas velocity and other necessary dimensioning will be based on a balance of safety against influx of contaminants through the seal under stationary and transient conditions, and to avoid unduly large dimensioning of the barrier gas supply system. It is particularly important to keep the supply pipe (e.g., the line 9) for barrier gas within a favourable diameter, for example, less than 25 mm, and also avoid the need for more than one feed pipe for one compressor station.
  • the supply pipe e.g., the line 9
  • barrier gas velocity of between 1 m/s and 5 m/s, depending upon the actual operating conditions, will normally result in protection against influx and buildup of harmful levels of contaminating gases, condensed water, hydrocarbon condensate and particles in the motor and magnetic bearings, whilst avoiding an unfavourably large barrier gas supply system. It is the chosen barrier gas velocity through the seal, based on an understanding of the mechanisms which may lead to the ingress of contaminated fluid through the seals, which forms the basis for the dimensioning of the supply and feed system and the control of the supply of barrier gas.
  • the compressor module will be positioned horizontally, and in that case particles/droplets have no velocity of fall in the direction of the seal.
  • the indicated (above) barrier gas velocities in the seal will in such cases provide extensive protection against contamination of the motor and seals under stationary operating conditions ("steady state").
  • Such a chosen barrier gas velocity will also impede particles that might be thrown against the seals by the rotating impellers and the shaft, because their momentum is quickly taken from them by the counter-flowing barrier gas and by the actual physical barrier formed by the seal.
  • Even under transient conditions for example, the starting and the stopping of the compressor module or on the shut-down or start-up of wells, there will be substantial protection against contamination. Even if gaseous contaminants were briefly to penetrate into the motor under transient conditions, they would be so diluted by the clean barrier gas in the motor that they would not reach harmful levels. The same applies to the build-up of particles.
  • the seal 31, 32 forms an annulus around the shaft 8. This annulus may typically have an aperture of about 0.3 mm.
  • a barrier gas velocity of 2.5 m/s
  • a shaft diameter of 150 mm
  • a gas pressure of 100 bars.
  • the barrier gas is methane gas.
  • the need for supply (in other words, mass flow, m) of barrier gas for a seal will be in the range of 0.0068 kg/s.
  • the need for barrier gas will be about 0.02 kg/s.
  • Such a low consumption of barrier gas will result in a favourable dimensioning of the supply system for barrier gas, including pipes in the umbilical, even with several compressor modules in a subsea compressor station.
  • the invention is thus based on utilising, in combination, the knowledge, of necessary barrier gas velocity, v g , through the seal; and knowledge of (measurement of) the pressure inside the compressor compartment facing the seals, p s , (normally equal to the suction pressure of the compressor) and of how this pressure falls over time.
  • a certain desired overpressure, p a can be set in an accumulator 6 which can be installed inside the barrier gas supply pipe 9, or the volume in the supply pipe may constitute an adequate accumulator; a controlled supply of barrier gas can be supplied to the compressor module (the first and optionally the third compartment) by means of a flow restriction 71, 71' in the feed pipe 7, 7', 7" between the accumulator 6 and the inlet to the first (optionally also the third) compartment which contains the motor and/or magnetic bearings.
  • the flow restriction is calibrated and/or controlled so that it gives a volume flow of barrier gas into the first (optionally also the third) compartment which at least provides the determined minimum barrier gas velocity through the seal.
  • the flow restriction may alternatively be calibrated and/or controlled so that it gives a fixed mass flow, i.e., a volume flow that increases as a function of falling suction pressure, p s , of barrier gas in the first (optionally also the third compartment) which at least gives the determined minimum barrier gas velocity through the seal.
  • a control is in practice very easy to obtain in a subsea system where T a will be constant (equal to the surrounding seawater temperature), by keeping p a constant over time irrespective of the value of p s .
  • a flow meter between the accumulator at p a and the flow restriction may then be controlled on a fixed signal, for example, fixed pressure drop through a metering orifice.
  • Mass flow and velocity through the supply pipe 9 will then be constant over time. Because the velocity v g of the barrier gas through the seal is low, the pressure drop across the seal will also be small.
  • the pressure inside the motor compartment and the bearing compartment (in other words, the first and third compartments) will only have a very small overpressure, ⁇ p (roughly in the range of 0.02 to 0.3 bar) in relation to the suction pressure, p s , of the compressor, and this fact is important for choosing the right value for the pressure in the accumulator, p a , which, for example, can be set at 5 to 50 bars or more above p s .
  • the pressure drop across the seal is therefore neglected in relation to the pressure drop across the flow restriction, and it is therefore in practice the flow restriction alone that determines the flow of barrier gas.
  • the above-mentioned accumulator 6 does not necessarily need to be a separate tank, but can in certain cases consist of the volume of compressed gas in the pipe ahead of the flow restriction 71, 71'. hi many cases it will, however, be advantageous to have a suitably dimensioned pressure tank as an accumulator near the flow restriction, as shown in Figure 1.
  • the flow restriction 71, 71' may be located in immediate proximity to the feed pipe 7, 7', 7" inlet into the compartment for the motor and seal, or it may be located many kilometres away. For subsea compressors, this may mean that under water and very close to the compressor module there is a flow restriction and an accumulator tank, and that the barrier gas is supplied through a supply pipe in the umbilical from a platform or the shore and at a pressure from the gas supply source that results in the desired pressure p a . For transport over long distances, it is advantageous that the flow restriction takes place close to the compressor module so that the transport of barrier gas takes place at maximum pressure to keep the diameter of the supply pipe as small as possible.
  • the feed of the desired volume flow of barrier gas can take place at relatively low pressure -just sufficient to overcome the friction in the pipe - direct from the barrier gas source, e.g., with a piston compressor which is set to give desired volume flow through the seal without having an accumulator and flow restriction close to the compressor module, or by the supply of desired volume flow from the shore or a platform in that the accumulator tank and mass flow control are located there.
  • the disadvantage of this will be that because of low gas pressure, i.e., expanded gas volume, the diameters of the feed pipe will have to be relatively large, and will thus be cost-increasing for the umbilical.
  • the flow restriction 71, 71' is shown in its most basic form in Figure 5, where a reservoir pressure (p a ) is controlled in one of several ways which will be described below, to the desired pressure in the first compartment (10), namely p s + ⁇ p .
  • Figure 3 shows a variant of the flow restriction 71; 71', where a choke (valve) 79 is controlled on the basis of flow measurement.
  • Figure 2 shows a further variant of the flow restriction 71 ; 71 ' which comprises a plurality of chokes 79' in parallel.
  • the control of the barrier gas flow has been described as a suitable flow restriction 71, 71' installed in the feed pipe 7, 7', 7" into the compartment or compartments for the motor and magnetic bearings, and this flow restriction restricts between on the one hand a known pressure, p s , (determined by the reservoir pressure at any given time and the drop in pressure up to the inlet of the compressor) and on the other hand a desired set pressure, p a , ahead of the flow restriction.
  • the supply of barrier gas to the "clean" compartments can in practice be controlled in several ways:
  • Allow P a to remain fixed, and calibrate and set a fixed flow restriction which gives minimum sufficient supply of barrier gas at the start of compression (i.e., at the start-up, in the early phase of the well), and which gives increasing consumption as the reservoir pressure (and thus also p s ) drops.
  • the volume flow of barrier gas, and thus the mass flow, increases by the square root of the difference p a -p s .
  • Fixed pa, adjustable flow restriction via valve o p a is fixed, and the flow restriction 71, 71' is adjustable, e.g., in the form of one or more valves which can be operated manually (e.g., by a person or using a remote operated vessel (ROV)) so that the flow restriction at certain intervals is increased as p s drops.
  • the flow restriction may be adjusted by, e.g., measuring the pressure drop across the flow restriction.
  • o p a is fixed, and the flow restriction 71, 71' is adjustable, e.g, in the form of a hydraulically operated valve which can be controlled manually from a control room so that the flow restriction at certain intervals is increased as p s drops.
  • the flow restriction may adjusted by, e.g., measuring the pressure drop across the flow restriction.
  • P a is fixed, and a flow control valve is installed that adjusts the flow on the basis of measured pressure drop across a restriction upstream of the valve and the measurement of the pressure and the temperature in the motor compartment and the magnetic bearing compartment, so that the valve produces a fixed volume flow, and thus a fixed desired set barrier gas velocity through the seal.
  • p a can be up-adjusted as required, e.g., 1 to 5 bars above the pressure in the inlet/outlet pipe on feed-in of gas from the supply source (on the shore or a platform).
  • WHSP Wellhead Shut-in Pressure
  • FIG. 6 shows a mechanical control device for barrier gas which gives constant mass flow when pressure and temperature upstream of the controller are constant.
  • the control device includes a valve housing 101 with an inlet 102 which is fluid-connected to a cavity in the valve housing where a piston 103 is located. As shown in the figure, there is a fixed opening 104 in the piston, or between the piston and the internal valve housing wall, through which opening gas can flow.
  • the piston 103 is connected to a spring 105 which in turn is fixed in a channel 109 in the valve housing.
  • the piston is also connected to a first pipe 111 that is coaxially arranged with and partly surrounds a second pipe 107.
  • the first pipe 111 is arranged in a separate channel 108 and can (together with the piston 103) slide back and forth over the second pipe 107.
  • the second pipe 107 is fluid-connected to an opening 110 in the valve housing and a part of the second pipe 107 that is on the downstream side of the piston 103 is provided with one or more openings 106 which thus create fluid connection between said cavity and said opening 110.
  • the opening 110 is, in use, in connection with the control device described above, an outlet for barrier gas into the motor compartment and the compartment for magnetic bearings.
  • a barrier gas at a pressure p a and constant temperature (temperature of surrounding seawater) will be passed into the inlet 102 and into the above-mentioned valve housing cavity.
  • a drop in pressure will occur. This drop in pressure will produce a force that will push the piston 103 and the first pipe 111 in the direction of the gas flow (towards the right in Figure 6).
  • the spring 105 will produce a counter-force that will push the piston 103 and the first pipe 111 in the direction of the gas flow (to the right in Figure 6).
  • the spring 105 can be adjusted so that the drop in pressure through the piston opening 104 remains fixed.
  • the piston 103 will be pushed all the way over to the left, which leads to the opening 106 in the second pipe 107 being opened fully. This will lead to the pressure in the whole system, including the compressor module, settling at p a .

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Abstract

La présente invention concerne un appareil de commande de l’alimentation en gaz barrière d’un module de compresseur, comprenant un carter sous pression (3) contenant un moteur électrique (1) relié par entraînement via un arbre (8) à un compresseur (2). L’arbre (8) est soutenu par des paliers magnétiques (11, 21) et au moins un joint de roulement axial (31) autour de l’arbre (8) qui sépare le carter sous pression en un premier compartiment (10) comprenant le moteur (1) et un second compartiment (20) comprenant le compresseur (2), le second compartiment (20) comprenant un orifice d’admission (4) et un orifice de refoulement (5) pour le fluide à compresser. Une conduite (7) est en communication fluidique avec le premier compartiment (10) pour l’alimentation en gaz barrière d’un réservoir (6) et un mécanisme de réduction du débit (71) est disposé dans la conduite entre le réservoir (6) et le premier compartiment (10). Ledit appareil facilite un procédé de commande de l’alimentation en gaz barrière sur la base de la vitesse de gaz barrière nécessaire (vg) à travers le joint de roulement (31; 32) et de la pression (ps) dans le second compartiment (20). Une surpression (pa) peut être établie dans le réservoir (6) et une alimentation commandée en gaz barrière du premier compartiment (10) au moins est obtenue à l’aide de la réduction du débit (71; 71') dans le tuyau d’alimentation (7; 7').
PCT/NO2006/000341 2005-10-07 2006-10-04 Appareil et procédé de commande de l’alimentation en gaz barrière dans un module de compresseur WO2007043889A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US12/089,413 US20080260539A1 (en) 2005-10-07 2005-10-07 Apparatus and Method For Controlling Supply of Barrier Gas in a Compressor Module
BRPI0616912-0A BRPI0616912A2 (pt) 2005-10-07 2006-10-04 aparelho e método para controlar a alimentação de gás barreira a um módulo compressor
CA002624785A CA2624785A1 (fr) 2005-10-07 2006-10-04 Appareil et procede de commande de l'alimentation en gaz barriere dans un module de compresseur
GB0805821A GB2444220B (en) 2005-10-07 2006-10-04 Apparatus and method for controlling supply of barrier gas in a compressor module

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
NO20054620A NO325900B1 (no) 2005-10-07 2005-10-07 Anordning og fremgangsmåte for regulering av tilførsel av barrieregass til en kompressormodul
NO20054620 2005-10-07

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Publication Number Publication Date
WO2007043889A1 true WO2007043889A1 (fr) 2007-04-19

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Cited By (36)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008002147A1 (fr) * 2006-06-30 2008-01-03 Aker Kvaerner Subsea As Appareil et procédé pour empêcher la pénétration de l'eau de mer dans un module de compresseur lors de l'abaissement vers le fond marin ou de l'extraction de celui-ci
GB2453313A (en) * 2007-08-04 2009-04-08 Waukesha Bearings Ltd Compressor bearing arrangement
EP2206927A1 (fr) * 2009-01-13 2010-07-14 Siemens Aktiengesellschaft Machine pour le transport de fluides
US8062400B2 (en) 2008-06-25 2011-11-22 Dresser-Rand Company Dual body drum for rotary separators
US8061737B2 (en) 2006-09-25 2011-11-22 Dresser-Rand Company Coupling guard system
US8061972B2 (en) 2009-03-24 2011-11-22 Dresser-Rand Company High pressure casing access cover
US8075668B2 (en) 2005-03-29 2011-12-13 Dresser-Rand Company Drainage system for compressor separators
US8079622B2 (en) 2006-09-25 2011-12-20 Dresser-Rand Company Axially moveable spool connector
US8079805B2 (en) 2008-06-25 2011-12-20 Dresser-Rand Company Rotary separator and shaft coupler for compressors
US8087901B2 (en) 2009-03-20 2012-01-03 Dresser-Rand Company Fluid channeling device for back-to-back compressors
US8210804B2 (en) 2009-03-20 2012-07-03 Dresser-Rand Company Slidable cover for casing access port
US8231336B2 (en) 2006-09-25 2012-07-31 Dresser-Rand Company Fluid deflector for fluid separator devices
US8267437B2 (en) 2006-09-25 2012-09-18 Dresser-Rand Company Access cover for pressurized connector spool
US8302779B2 (en) 2006-09-21 2012-11-06 Dresser-Rand Company Separator drum and compressor impeller assembly
NO327557B2 (no) * 2007-10-09 2013-02-04 Aker Subsea As Beskyttelsessystem for pumper
US8408879B2 (en) 2008-03-05 2013-04-02 Dresser-Rand Company Compressor assembly including separator and ejector pump
US8414692B2 (en) 2009-09-15 2013-04-09 Dresser-Rand Company Density-based compact separator
US8430433B2 (en) 2008-06-25 2013-04-30 Dresser-Rand Company Shear ring casing coupler device
US8434998B2 (en) 2006-09-19 2013-05-07 Dresser-Rand Company Rotary separator drum seal
US20130136629A1 (en) * 2011-06-01 2013-05-30 Dresser-Rand Company Subsea motor-compressor cooling system
US8596292B2 (en) 2010-09-09 2013-12-03 Dresser-Rand Company Flush-enabled controlled flow drain
US8657935B2 (en) 2010-07-20 2014-02-25 Dresser-Rand Company Combination of expansion and cooling to enhance separation
US8663483B2 (en) 2010-07-15 2014-03-04 Dresser-Rand Company Radial vane pack for rotary separators
US8673159B2 (en) 2010-07-15 2014-03-18 Dresser-Rand Company Enhanced in-line rotary separator
AU2009244519B2 (en) * 2008-05-06 2014-04-03 Fmc Technologies, Inc. Flushing system
US8696331B2 (en) 2008-05-06 2014-04-15 Fmc Technologies, Inc. Pump with magnetic bearings
US8733726B2 (en) 2006-09-25 2014-05-27 Dresser-Rand Company Compressor mounting system
US8746464B2 (en) 2006-09-26 2014-06-10 Dresser-Rand Company Static fluid separator device
US8821362B2 (en) 2010-07-21 2014-09-02 Dresser-Rand Company Multiple modular in-line rotary separator bundle
US8851756B2 (en) 2011-06-29 2014-10-07 Dresser-Rand Company Whirl inhibiting coast-down bearing for magnetic bearing systems
US8876389B2 (en) 2011-05-27 2014-11-04 Dresser-Rand Company Segmented coast-down bearing for magnetic bearing systems
US8994237B2 (en) 2010-12-30 2015-03-31 Dresser-Rand Company Method for on-line detection of liquid and potential for the occurrence of resistance to ground faults in active magnetic bearing systems
US9024493B2 (en) 2010-12-30 2015-05-05 Dresser-Rand Company Method for on-line detection of resistance-to-ground faults in active magnetic bearing systems
US9095856B2 (en) 2010-02-10 2015-08-04 Dresser-Rand Company Separator fluid collector and method
US9551349B2 (en) 2011-04-08 2017-01-24 Dresser-Rand Company Circulating dielectric oil cooling system for canned bearings and canned electronics
EP2358975A4 (fr) * 2008-11-12 2017-04-12 Exxonmobil Upstream Research Company Procedes et systemes a compresseur de recipient

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8641395B2 (en) * 2009-04-03 2014-02-04 Johnson Controls Technology Company Compressor
NO332973B1 (no) * 2010-06-22 2013-02-11 Vetco Gray Scandinavia As Trykkreguleringssystem for motor- og pumpebarrierefluider med differensialtrykkstyring
NO332972B1 (no) * 2010-06-22 2013-02-11 Vetco Gray Scandinavia As Trykkreguleringssystem for motor- og pumpebarrierefluider i en undersjoisk motor- og pumpemodul
EP2633198A4 (fr) * 2010-10-27 2017-01-11 Dresser-Rand Company Système et procédé permettant la mise sous pression rapide d'un moteur/circuit de refroidissement pour un système de moteur/compresseur étanche
NO333684B1 (no) 2011-03-07 2013-08-12 Aker Subsea As Undervanns trykkøkningsmaskin
RU2472043C1 (ru) * 2011-07-28 2013-01-10 Закрытое акционерное общество "Научно-исследовательский и конструкторский институт центробежных и роторных компрессоров им. В.Б. Шнеппа" Центробежный компрессорный агрегат
WO2013028594A2 (fr) * 2011-08-24 2013-02-28 Dresser-Rand Company Système de compression sous-marin efficace et fiable
US9482345B2 (en) * 2012-10-04 2016-11-01 Sulzer Management Ag Sealing arrangement for a rotating shaft
NO334805B1 (no) * 2012-12-11 2014-06-02 Aker Subsea As Trykk - volum regulator
US9664418B2 (en) 2013-03-14 2017-05-30 Johnson Controls Technology Company Variable volume screw compressors using proportional valve control
US11378083B2 (en) * 2017-01-24 2022-07-05 Onesubsea Ip Uk Limited Mechanical barrier fluid pressure regulation for subsea systems
BR102017009824B1 (pt) 2017-05-10 2023-12-19 Fmc Technologies Do Brasil Ltda Sistema para circulação de gás em espaços anulares de máquinas rotativas
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US20230151818A1 (en) * 2021-11-16 2023-05-18 Carrier Corporation Compressor assembly including a flow-restricting valve

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5280766A (en) * 1990-06-26 1994-01-25 Framo Developments (Uk) Limited Subsea pump system
US5382141A (en) * 1991-02-08 1995-01-17 Kvaener Rosenberg A.S. Kvaerner Subsea Contracting Compressor system and method of operation
US5412977A (en) * 1992-07-02 1995-05-09 Sulzer Escher Wyss Ag Turbo machine with an axial dry gas seal
US6827974B2 (en) * 2002-03-29 2004-12-07 Pilkington North America, Inc. Method and apparatus for preparing vaporized reactants for chemical vapor deposition
WO2005003512A1 (fr) * 2003-07-02 2005-01-13 Kvaerner Oilfield Products As Module de compresseur sous-marin et procede pour commander la pression dans un tel module de compresseur sous-marin

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH423075A (de) * 1965-05-18 1966-10-31 Bbc Brown Boveri & Cie Verfahren zum Betrieb eines gekapselten Gebläses
US3968388A (en) * 1972-06-14 1976-07-06 Kraftwerk Union Aktiengesellschaft Electric machines, particularly turbogenerators, having liquid cooled rotors
US4606652A (en) * 1984-06-20 1986-08-19 Rotoflow, Corporation Shaft seal for turbomachinery
US4681559A (en) * 1985-12-23 1987-07-21 Cordis Corporation Plural valve three stage pressure relief system
GB8921071D0 (en) * 1989-09-18 1989-11-01 Framo Dev Ltd Pump or compressor unit
US5063956A (en) * 1990-10-31 1991-11-12 Union Carbide Industrial Gases Technology Corporation Fluid delivery pressure control system
JP2998441B2 (ja) * 1992-08-19 2000-01-11 株式会社日立製作所 ターボ真空ポンプ
DE19523713C2 (de) * 1995-06-22 1997-04-24 Mannesmann Ag Verfahren und Vorrichtung zur Sicherung der Funktionstüchtigkeit von Gasdichtungen bei Turboverdichtern
US5636847A (en) * 1995-09-13 1997-06-10 Chesterton International Company Dual face seal clean barrier fluid and dynamic pressure control system
US5769427A (en) * 1995-09-13 1998-06-23 Chesterton International Company Dual seal with clean barrier fluid and dynamic pressure control
DE19738122A1 (de) * 1997-09-01 1999-03-11 Waeschle Maschf Gmbh Zellenradschleuse zum Dosieren von Schüttgut
GB0004239D0 (en) * 2000-02-24 2000-04-12 Crane John Uk Ltd Seal assemblies
DE10042962C1 (de) * 2000-08-31 2002-05-02 Siemens Ag Magnetlager zur Lagerung einer drehbaren Welle unter Verwendung von Hoch-T¶c¶-Supraleitermaterial
US7217469B2 (en) * 2003-05-27 2007-05-15 General Motors Corporation Fluid handling device for hydrogen-containing process fluids

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5280766A (en) * 1990-06-26 1994-01-25 Framo Developments (Uk) Limited Subsea pump system
US5382141A (en) * 1991-02-08 1995-01-17 Kvaener Rosenberg A.S. Kvaerner Subsea Contracting Compressor system and method of operation
US5412977A (en) * 1992-07-02 1995-05-09 Sulzer Escher Wyss Ag Turbo machine with an axial dry gas seal
US6827974B2 (en) * 2002-03-29 2004-12-07 Pilkington North America, Inc. Method and apparatus for preparing vaporized reactants for chemical vapor deposition
WO2005003512A1 (fr) * 2003-07-02 2005-01-13 Kvaerner Oilfield Products As Module de compresseur sous-marin et procede pour commander la pression dans un tel module de compresseur sous-marin

Cited By (45)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8075668B2 (en) 2005-03-29 2011-12-13 Dresser-Rand Company Drainage system for compressor separators
GB2453690A (en) * 2006-06-30 2009-04-15 Aker Kvaerner Subsea As Apparatus and method for preventing the penetration of seawater into a compressor module lowering to or retrieval from the seabed
US8267676B2 (en) 2006-06-30 2012-09-18 Aker Subsea As Apparatus and method for preventing the penetration of seawater into a compressor module during lowering to or retrieval from the seabed
WO2008002147A1 (fr) * 2006-06-30 2008-01-03 Aker Kvaerner Subsea As Appareil et procédé pour empêcher la pénétration de l'eau de mer dans un module de compresseur lors de l'abaissement vers le fond marin ou de l'extraction de celui-ci
GB2453690B (en) * 2006-06-30 2011-03-23 Aker Kvaerner Subsea As Apparatus and method for preventing the penetration of seawater into a compressor module during lowering to or retrieval from the seabed
US8434998B2 (en) 2006-09-19 2013-05-07 Dresser-Rand Company Rotary separator drum seal
US8302779B2 (en) 2006-09-21 2012-11-06 Dresser-Rand Company Separator drum and compressor impeller assembly
US8079622B2 (en) 2006-09-25 2011-12-20 Dresser-Rand Company Axially moveable spool connector
US8061737B2 (en) 2006-09-25 2011-11-22 Dresser-Rand Company Coupling guard system
US8733726B2 (en) 2006-09-25 2014-05-27 Dresser-Rand Company Compressor mounting system
US8231336B2 (en) 2006-09-25 2012-07-31 Dresser-Rand Company Fluid deflector for fluid separator devices
US8267437B2 (en) 2006-09-25 2012-09-18 Dresser-Rand Company Access cover for pressurized connector spool
US8746464B2 (en) 2006-09-26 2014-06-10 Dresser-Rand Company Static fluid separator device
GB2453313A (en) * 2007-08-04 2009-04-08 Waukesha Bearings Ltd Compressor bearing arrangement
GB2453313B (en) * 2007-08-04 2012-06-27 Waukesha Bearings Ltd Motor compressor
US8556600B2 (en) 2007-10-09 2013-10-15 Aker Subsea As Protection system for subsea seawater injection pumps
NO327557B2 (no) * 2007-10-09 2013-02-04 Aker Subsea As Beskyttelsessystem for pumper
US8408879B2 (en) 2008-03-05 2013-04-02 Dresser-Rand Company Compressor assembly including separator and ejector pump
US8777596B2 (en) 2008-05-06 2014-07-15 Fmc Technologies, Inc. Flushing system
US9601964B2 (en) 2008-05-06 2017-03-21 Fmc Technologies, Inc. In-line flow mixer
AU2009244519B2 (en) * 2008-05-06 2014-04-03 Fmc Technologies, Inc. Flushing system
US8696331B2 (en) 2008-05-06 2014-04-15 Fmc Technologies, Inc. Pump with magnetic bearings
US8079805B2 (en) 2008-06-25 2011-12-20 Dresser-Rand Company Rotary separator and shaft coupler for compressors
US8062400B2 (en) 2008-06-25 2011-11-22 Dresser-Rand Company Dual body drum for rotary separators
US8430433B2 (en) 2008-06-25 2013-04-30 Dresser-Rand Company Shear ring casing coupler device
EP2358975A4 (fr) * 2008-11-12 2017-04-12 Exxonmobil Upstream Research Company Procedes et systemes a compresseur de recipient
EP2206927A1 (fr) * 2009-01-13 2010-07-14 Siemens Aktiengesellschaft Machine pour le transport de fluides
WO2010081763A1 (fr) * 2009-01-13 2010-07-22 Siemens Aktiengesellschaft Machine destinée au transport de fluide
US8210804B2 (en) 2009-03-20 2012-07-03 Dresser-Rand Company Slidable cover for casing access port
US8087901B2 (en) 2009-03-20 2012-01-03 Dresser-Rand Company Fluid channeling device for back-to-back compressors
US8061972B2 (en) 2009-03-24 2011-11-22 Dresser-Rand Company High pressure casing access cover
US8414692B2 (en) 2009-09-15 2013-04-09 Dresser-Rand Company Density-based compact separator
US9095856B2 (en) 2010-02-10 2015-08-04 Dresser-Rand Company Separator fluid collector and method
US8663483B2 (en) 2010-07-15 2014-03-04 Dresser-Rand Company Radial vane pack for rotary separators
US8673159B2 (en) 2010-07-15 2014-03-18 Dresser-Rand Company Enhanced in-line rotary separator
US8657935B2 (en) 2010-07-20 2014-02-25 Dresser-Rand Company Combination of expansion and cooling to enhance separation
US8821362B2 (en) 2010-07-21 2014-09-02 Dresser-Rand Company Multiple modular in-line rotary separator bundle
US8596292B2 (en) 2010-09-09 2013-12-03 Dresser-Rand Company Flush-enabled controlled flow drain
US8994237B2 (en) 2010-12-30 2015-03-31 Dresser-Rand Company Method for on-line detection of liquid and potential for the occurrence of resistance to ground faults in active magnetic bearing systems
US9024493B2 (en) 2010-12-30 2015-05-05 Dresser-Rand Company Method for on-line detection of resistance-to-ground faults in active magnetic bearing systems
US9551349B2 (en) 2011-04-08 2017-01-24 Dresser-Rand Company Circulating dielectric oil cooling system for canned bearings and canned electronics
US8876389B2 (en) 2011-05-27 2014-11-04 Dresser-Rand Company Segmented coast-down bearing for magnetic bearing systems
US9206819B2 (en) * 2011-06-01 2015-12-08 Dresser-Rand Company Subsea motor-compressor cooling system
US20130136629A1 (en) * 2011-06-01 2013-05-30 Dresser-Rand Company Subsea motor-compressor cooling system
US8851756B2 (en) 2011-06-29 2014-10-07 Dresser-Rand Company Whirl inhibiting coast-down bearing for magnetic bearing systems

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US20080260539A1 (en) 2008-10-23
BRPI0616912A2 (pt) 2013-01-01
GB0805821D0 (en) 2008-04-30
NO20054620L (no) 2007-04-10
NO20054620D0 (no) 2005-10-07
CA2624785A1 (fr) 2007-04-19
RU2008118142A (ru) 2009-11-20
NO325900B1 (no) 2008-08-11
GB2444220A (en) 2008-05-28
GB2444220B (en) 2011-05-11
RU2427704C2 (ru) 2011-08-27

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