EP2980348B1 - Dispositif de séparation destiné à séparer des particules de matière solide d'écoulements gazeux et liquides pour des pressions différentielles élevées - Google Patents

Dispositif de séparation destiné à séparer des particules de matière solide d'écoulements gazeux et liquides pour des pressions différentielles élevées Download PDF

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Publication number
EP2980348B1
EP2980348B1 EP14179128.5A EP14179128A EP2980348B1 EP 2980348 B1 EP2980348 B1 EP 2980348B1 EP 14179128 A EP14179128 A EP 14179128A EP 2980348 B1 EP2980348 B1 EP 2980348B1
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EP
European Patent Office
Prior art keywords
ring stack
separating device
spacers
annular
annular disks
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.)
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Application number
EP14179128.5A
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German (de)
English (en)
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EP2980348A1 (fr
Inventor
Dietrich Lange
Alexander Krecker
Christoph Lesniak
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3M Innovative Properties Co
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3M Innovative Properties Co
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Publication date
Priority to DK14179128.5T priority Critical patent/DK2980348T3/en
Application filed by 3M Innovative Properties Co filed Critical 3M Innovative Properties Co
Priority to ES14179128.5T priority patent/ES2640477T3/es
Priority to EP14179128.5A priority patent/EP2980348B1/fr
Priority to AU2015296866A priority patent/AU2015296866B2/en
Priority to MX2017001260A priority patent/MX2017001260A/es
Priority to CN201580041600.5A priority patent/CN106574494B/zh
Priority to PCT/US2015/042288 priority patent/WO2016018821A1/fr
Priority to US15/329,983 priority patent/US10415351B2/en
Priority to RU2017102753A priority patent/RU2645393C1/ru
Priority to CA2956483A priority patent/CA2956483A1/fr
Priority to BR112017001857A priority patent/BR112017001857A2/pt
Publication of EP2980348A1 publication Critical patent/EP2980348A1/fr
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Publication of EP2980348B1 publication Critical patent/EP2980348B1/fr
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    • 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
    • E21B43/02—Subsoil filtering
    • E21B43/08—Screens or liners
    • E21B43/086—Screens with preformed openings, e.g. slotted liners
    • 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
    • E21B43/02—Subsoil filtering
    • E21B43/08—Screens or liners
    • E—FIXED CONSTRUCTIONS
    • E03—WATER SUPPLY; SEWERAGE
    • E03B—INSTALLATIONS OR METHODS FOR OBTAINING, COLLECTING, OR DISTRIBUTING WATER
    • E03B3/00—Methods or installations for obtaining or collecting drinking water or tap water
    • E03B3/06—Methods or installations for obtaining or collecting drinking water or tap water from underground
    • E03B3/08—Obtaining and confining water by means of wells
    • E03B3/16—Component parts of wells
    • E03B3/18—Well filters

Definitions

  • the present invention relates to a novel high differential pressure separator capable of separating undesired solid particles from a volume flow of oil, gas and water or mixtures thereof.
  • Such separators are needed in many oil and gas wells. Petroleum and natural gas are stored in natural subterranean deposits, with the oil or gas being distributed in more or less porous and permeable mineral layers. The aim of any oil or gas well is to reach and exploit the occurrence so that only salable products such as oil and gas are promoted, but unwanted by-products are minimized or even completely avoided. Undesirable by-products of oil and gas extraction include particulate matter such as sands and other mineral particles entrained in the borehole by the flow of liquid or gas from the deposit. Depending on the permeability of the geological layer and the reservoir pressure, the flow rates of the solids-laden liquid and gas flow can be very high, up to 15 m / sec and in some cases higher.
  • Abrasion and erosion problems in the separation of solid particles from liquid and gas flows are not limited to the oil and gas industry, but can also occur in the promotion of water.
  • Water can be extracted for the purpose of drinking water production or geothermal energy production.
  • the porous, often loosely layered deposits of water tend to introduce a significant amount of abrasive particles into the conveyed material. Also in these applications there is a need for abrasion and erosion resistant filters.
  • filters are used today for the separation of unwanted particles, which are produced by spiral winding and welding of steel form wires onto a perforated base pipe. Such filters are referred to as “wire wrap filters”.
  • Another common design for filters in the oil and gas production is the wrapping of a perforated base pipe with steel screen meshes. These filters are referred to as "metal mesh screen”. Both processes produce filters with effective sieve openings of 75 ⁇ m to 350 ⁇ m.
  • the filter elements are additionally protected by an externally mounted, coarse mesh cage from mechanical damage during transport and insertion into the borehole.
  • a disadvantage of these types of filters is that steel structures under the action of high-speed abrasive particles are subject to a rapid abrasion wear, which quickly leads to the destruction of filigree sieve structures. Such fast abrasive flows often occur in oil and / or gas wells, resulting in a high technical and financial maintenance effort when changing the filter. There are even production wells which, for reasons of these flows, can not be controlled with conventional filter technology and therefore can not be economically exploited.
  • Conventional metallic filters are subject to abrasion and erosion wear because steels, even when cured, are softer than the partially quartz-containing particles in the production wells.
  • WO 2011/009 469 A1 and WO 2011/120 539 A1 Filter constructions are proposed in which the filter gaps, so the function openings of the filter, are produced by stacking specially shaped densely sintered annular discs of a brittle-hard material, preferably of a ceramic material. At the same time, at least three spacers distributed uniformly over the circumference of the disks are arranged on the upper side of annular disks and the disks are stacked on top of one another so that the spacers lie one above the other.
  • the spacers are in the form of spherical sections.
  • the formation of the spacers in the form of spherical sections is disadvantageous in that the against Abrasion and erosion of very well resistant ceramic materials such as densely sintered silicon carbide are sensitive to punctiform pressure loading and fail in case of overuse due to the punctiform pressure load due to breakage.
  • High punctiform contact stresses are referred to as Hertzian pressure. In the material volume below the point under compression occurs due to the punctiform pressure load to high tensile stresses that can lead to breakage of the ceramic rings.
  • the separator experiences only insignificant pressure differences between the inlet and outlet side of the filter. This is true as long as the separator is not added, d. H. is clogged and can be flowed through more or less freely.
  • the pressure differences or pressure losses in the separator are low under normal operating conditions. But if the filter gaps are added, the pressure differences can increase very much.
  • the clogging or clogging of the separating device can be caused by undesired settling of mineral particles at the inlet opening of the filter, that is to say at the annular gaps on the outer circumferential surface of the annular stack.
  • the risk of addition depends inter alia on the particle size distribution of the mineral particle-liquid mixture and the flow velocity at the location of the filter.
  • the clogging or clogging of the separator may, on the other hand, be caused by intentional filling of highly viscous solids laden liquids into the wellbore. Such a fluid is referred to as a "fluid loss control pill”.
  • An added or clogged filter may now be exposed to very high pressure differentials depending on the downhole operating conditions, which are on the order of 2500 psi (equivalent to 172 bar or 17.2 MPa) external pressure, ie external pressurization, and 1000 psi 69 bar or 6.9 MPa) internal pressure, ie when pressure is applied from the inside.
  • For external pressure load occurs, for example, when adding the filter by unwanted setting of mineral particles at the inlet of the filter
  • For internal pressure load occurs, for example, during cleaning rinse the added filter.
  • WO 2011/009 469 A1 and WO 2011/120 539 A1 proposed filter on internal and external pressure-load capacity (burst pressure test, collapse pressure test) according to ISO 17824 and also in production use pressure conditions can occur, which lead to very high axial forces in the ceramic ring stacks. Even at comparatively low isostatic pressures, the axial forces can increase to such an extent that it is due to the Hertzian pressure due to the punctiform contact on the ball sections to break the rings comes.
  • WO 2011/009 469 A1 and WO 2011/120 539 A1 proposed constructions relates to the compression springs. These designed as coil springs compression springs are designed to keep the bias of the ceramic annular discs in changing environmental conditions, especially when changing the temperature constant. The intended effect of the distributed over the circumference of the annular discs springs is to keep the rings together with a largely independent of environmental influences force and so to keep the filter gap width constant. However, under certain operating conditions that may occur in the actual conveying operation of the filters, the springs behave differently than desired.
  • the annular discs are used in the DE 10 2008 057 894 A1 .
  • WO 2011/009 469 A1 and WO 2011/120 539 A1 stacked so that the spherical section spacers must each lie over each other.
  • This technical solution has drawbacks to the effect that on the one hand the assembly is complex, since care must be taken to the exact orientation of the rings, also there is a risk that the filter is rendered inoperative when the rings rotate due to transport or operational influences.
  • WO 2011/009 469 A1 The brittle-hard annular discs on the inner peripheral surface grooves for receiving guide rods, which serve during assembly for aligning and guiding the ring elements.
  • the brittle disks of the stack of rings are held together by longitudinal axis-parallel clamping rods located within the stack of rings or a clamping pipe located within the stack of rings.
  • the brittle discs On the inner circumferential surface, the brittle discs have recesses or grooves for receiving the tension rods.
  • a wear resistant separator for the separation of solid particles from liquids, particularly oil, gas and water, from production wells having high resistance to pressure differences between inlet and outlet sides of the separator. Furthermore, it is desirable that the separator temperature differences of at least 190 ° C, d. H. in the range of +10 ° C to +200 ° C, can withstand damage during operation and without impairing its functionality. Furthermore, the separator should survive the occurring during transport and storage low temperatures of up to -30 ° C harmless. Furthermore, it is desirable that the separation device can be used in curved production wells, is mechanically robust and meets the high requirements in terms of safety and reliability of the oil and gas industry.
  • the present invention provides a separating device according to claims 1 and 2 and their use according to claim 23.
  • Preferred or particularly expedient embodiments of the separation device are specified in the subclaims 3 to 22.
  • the invention further relates to the use of the separation device according to the invention for the separation of solid particles from liquids and / or gases in a process for the promotion of liquids and / or gases from production wells.
  • the invention further relates to the use of the separation device according to the invention for the separation of solid particles from liquids and / or gases in natural waters or in storage facilities for liquids and / or gases.
  • the separator according to the invention has a good resistance to pressure differences. It can withstand external pressures of up to 500 bar (or 50 MPa or 7250 psi) and more in the collapse pressure test to ISO 17824 and internal pressures of up to 120 bar (or 12 MPa or 1740 psi) and more Burst pressure test according to ISO 17824 without endangering its functionality. In these tests for internal and external pressure resistance, it does not break one of the brittle-hard annular discs.
  • the internal and external pressure resistance of the invention Separator is thus significantly larger than in the separation devices according to DE 10 2008 057 894 A1 .
  • WO 2011/009 469 A1 and WO 2011/120 539 A1
  • the annular discs Due to the flat contact surfaces of the spacers, the annular discs have a surface contact with the respective adjacent annular discs. This punctiform pressure loads are avoided, so that the risk of overuse by the Hertzian pressure and the fracture of the brittle-hard annular discs is significantly reduced compared to the separation devices of DE 10 2008 057 894 A1 .
  • the separating device according to the invention has no resilient-elastic construction elements such as springs, rubber discs or other elastic elements which cause a bias.
  • the ring stack of the separation device is not tensioned by compression springs, but fixed on the located inside the ring stack perforated tube without the ring stack undergoes a significant bias. By dispensing with the compression springs, it can not lead to tilting of the annular discs.
  • axial forces arise on the annular discs due to the fluid pressure, which can act on all sides in the filter gap and tries to push the annular discs apart.
  • the axial forces may occur at a smaller or larger number of annular discs.
  • the separation device according to the invention is supported by the support of the annular discs against each other and the support of the ring stack against the end caps, that it comes through the axial forces occurring under pressure to a measurable displacement of the annular discs in the axial direction. Even at high pressure differences due to internal or external pressure load, the filter gaps do not change in an undesirable manner, so that the filter effect is maintained even at high pressure differences.
  • the axial projection of the annular disks is circular at the inner and outer peripheries.
  • the annular discs therefore have, in contrast to those in DE 10 2008 057 894 A1 .
  • WO 2011/009 469 A1 and WO 2011/120 539 A1 proposed separation devices on no strength-reducing grooves or recesses on its inner and outer peripheral surface. Due to the ideal circular shape from a constructive point of view, stress concentrations due to pressure loading are largely avoided. As a result, the internal and external pressure load capacity of the separator is higher.
  • the production of the annular discs used for the separating device according to the invention can be realized inexpensively for different filter widths with a single pressing tool and the exact adjustment of the filter width can be done by hard machining of the sintered annular discs. For example, with a single pressing tool filter widths of 10 to 500 microns can be produced, resulting in significant savings in tooling costs and warehousing.
  • the annular discs are movable against each other to a certain extent, whereby the separator can also be introduced into curved delivery holes.
  • the separation device according to the invention constructed of brittle-hard ring elements is more abrasion and corrosion resistant than conventional metallic filters. It therefore has a longer service life under corrosive and abrasive conditions than conventional filters.
  • FIG. 1 shows the overall view of a separating device according to the invention. At both ends of the perforated tube 1 usually threaded 2 are attached, via which the separator can be connected to other components, either with other separation devices or with other components of the conveyor equipment.
  • top and bottom are used here, but the separator can also be positioned in a horizontal orientation in the production well.
  • FIGS. 6 a - 6 g and 8 a - 8 g show two preferred embodiments of the annular discs 8 used for the separating device according to the invention.
  • Figure block 6 shows the design of the annular discs for an embodiment with 15 spacers on top of the annular disc.
  • Figure 8 shows the design of the annular discs for an embodiment with 24 spacers on top of the annular disc.
  • the FIGS. 6 a and 8 a each show a plan view of the annular disc 8
  • the FIGS. 6b and 8b each show a cross-sectional view along the in FIG FIG. 6 a or 8 a with "6 b" or "8 b" designated cutting line.
  • FIGS. 6b or 8 b show enlarged sections of the cross-sectional views of FIGS. 6b or 8 b
  • the Figures 6f and 8f each show a 3D representation along the in FIG. 6 a and 8 a with "6 f" and "8 f" designated cutting line
  • the Figures 6g and 8g each show a 3D view of the annular disc.
  • the in the Figures 6a - 6g and 8a - 8g illustrated embodiment of the spacers is a preferred form of the spacers.
  • the annular discs are made of a brittle-hard material, preferably made of a ceramic material that is resistant to abrasion and erosion against solid particles such as sands and other mineral particles and corrosion resistant against the pumped media and the media used for maintenance, such as acids.
  • FIGS. 7 a - 7 f show schematically one of annular discs 8 of FIGS. 6 a - 6 g built ring stack.
  • FIG. 7 a shows a top view of the ring stack
  • FIG. 7 b shows a cross-sectional view taken along in FIG FIG. 7 a with "7 b" designated cutting line.
  • the FIGS. 7c and 7d show enlarged sections of the cross-sectional view of FIG. 7 b.
  • Figure 7e shows a 3D view of the ring stack
  • Figure 7f shows a 3D representation along the in FIG. 7 a with "7 f" designated cutting line.
  • the separation of the solid particles takes place at the inlet opening of an annular, preferably in the flow direction divergent, ie opening gap 14 (see Figures 7b and 7d ), which forms between two superimposed ring elements.
  • the ring elements are designed ceramics suitable or brittle-hard materials justice, ie cross-sectional transitions are performed without notches and the formation of bending stresses is largely avoided constructively.
  • the annular discs 8 (see figure blocks 6 and 8) have on their top 9 at least three evenly distributed over the circumference of the discs spacers 10 with a defined height, with the aid of the height of the separation gap 14 (gap width of the filter gap, filter width) is set.
  • the spacers are not separately applied or subsequently welded spacers. They are formed directly during manufacture during the shaping of the annular discs.
  • the annular discs are thus monolithic bodies and the spacers have the same high abrasion, erosion and corrosion resistance as the annular discs.
  • the contact surface 11 of the spacers 10 is flat (see Figures 6c . 6f . 8c and 8f ), so that the spacers 10 have a surface contact with the adjacent annular disc.
  • the annular discs 8 are in the region of the contact surface 11 of the spacers 10, ie in the region of contact with the adjacent annular disc 8, plane-parallel to the bottom 12 of the annular discs 8.
  • the bottom 12 of the annular discs is smooth and flat and at right angles to the disc axis educated.
  • the top 9 of the annular discs is preferably sloping inwardly or outwardly in the areas between the spacers, more preferably sloping inwardly.
  • the line of intersection on the top of the annular cross section of the annular discs is straight and the annular cross section of the annular discs is trapezoidal in the portions between the spacers. please refer FIGS. 6d and 8d ), wherein the thicker side of the ring cross-section must lie at the respective inlet side of the flow to be filtered.
  • the thickest point of the trapezoidal cross section must be on the outside and the upper side of the annular disks is sloping inward. If the flow to be filtered comes from the direction of the inner peripheral surface of the ring stack, then the thickest point of the trapezoidal cross-section must lie inside, and the upper side of the annular disks is sloping outwards.
  • a separator with divergent filter gap formed in this way is less susceptible to clogging and clogging than a separator in which the filter gaps have a filter aperture that is constant over the annular cross-section, ie where the ring tops and ring bottoms are parallel.
  • the outer contours of the annular discs are designed with a chamfer 13, as in the Figures 6c - 6e and 8c - 8e illustrated. It is also possible to make the annular discs with rounded edges. This represents an even better protection of the edges from the edge load which is critical for brittle-hard materials.
  • peripheral surfaces (lateral surfaces) of the annular discs are preferably cylindrical. But it is also possible to form the peripheral surfaces outwardly convex, for example, in order to achieve a better flow.
  • the annular discs are made with an outer diameter which is adapted to the provided in the application well of the production well, so that the separator according to the invention are introduced with little play in the wellbore can make the best possible use of the cross section of the production well to achieve a high flow rate.
  • the outer diameter of the annular discs can be 20-250 mm, but larger outer diameters than 250 mm are possible.
  • the radial ring width of the annular discs is preferably in the range of 8-20 mm. These ring widths are suitable for separation devices with base pipe diameters in the range 2 3/8 to 51 ⁇ 2 inches.
  • the axial thickness of the annular discs is preferably 3 to 12 mm, more preferably 4 to 7 mm.
  • the axial thickness or base thickness of the annular discs is measured in the area between the spacers and in trapezoidal cross-section on the thicker side in the area between the spacers.
  • the axial thickness of the annular discs in the region of the spacers corresponds to the sum of base thickness, d. H. the axial thickness of the annular discs in the area between the spacers, and the filter width.
  • the height of the spacers determines the filter width of the separator, so the separation gap between the individual annular discs.
  • the filter width determines which particle sizes of the solid particles to be separated, such as sand and rock particles, are transmitted by the separator and which particle sizes are not transmitted.
  • the height of the spacers is adjusted in the production of the annular discs targeted.
  • the filter width of the ring stack can be set to values between 10 ⁇ m and 5000 ⁇ m, preferably to values between 20 ⁇ m and 1000 ⁇ m and particularly preferably to values between 50 ⁇ m and 500 ⁇ m.
  • the deviation of the annular disks from the ideal circular shape at the inner and outer circumference is preferably ⁇ 0.5%, based on the outer diameter of the ring.
  • the roundness of the rings should be less than 0.5% of 170 mm, ie less than 0 , 85 mm.
  • the spacers arranged on the upper side of the annular disks have a surface contact with the adjacent annular disk.
  • the spacers allow a radial flow and are therefore preferably arranged radially aligned on the top of the annular discs.
  • the spacers can also be aligned at an angle to the radial direction.
  • the spacers disposed on top of the annular discs may extend over the entire radial width of the annular discs. But it is also possible that the spacers are formed so that they do not extend over the entire radial width of the surface of the annular discs, but that they occupy only a portion of this width. In this case, the spacers preferably occupy the part of the width of the annular discs, which is located on the filter outlet side of the annular discs, which is usually located on the inner periphery of the annular discs. If the spacers occupy only a portion of the width of the annular discs, an increase in the number of spacers is not necessarily associated with an undesirable decrease in the filter inlet area.
  • spacers are advantageous in that with almost the same support effect of the spacer, the annular inlet gap of the filter through the spacers is not or only slightly reduced, resulting in the desired high filter inlet area.
  • the separator can be made smaller, which favors its economic attractiveness and installation in confined spaces.
  • spacers occupying only a portion of the radial width of the surface of the annular discs are placed on the annular discs in alternation with such spacers extending over the entire radial width.
  • This is in the Figures 9 a and 9 c - 9 e. Shown here is a section of the top of an annular disc.
  • transitions between the top of the annular discs and the spacers are preferably not stepped or sharp-edged. Rather, the transitions between the top of the annular discs and the spacers are designed ceramic, ie the transitions are performed with radii, so gently rounded. This is in the Figures 6f and 8f illustrated.
  • the contact surface 11 of the spacers 10, so the flat surface with which the spacers are in contact with the adjacent annular disc may be rectangular, round, diamond-shaped, elliptical, trapezoidal or triangular, the shape of the corners and edges always ceramic appropriate, ie should be rounded.
  • Different versions of the spacers with different contact surfaces 11 are in the Figures 9 a - 9 e are shown.
  • FIG. 9 a One possible embodiment of spacers occupying only part of the radial width of the surface of the annular discs is shown FIG. 9 a.
  • shape of the spacer is approximately triangular, ie triangular with ceramic rounded corners. This shape is advantageously designed so that the flow cross-section does not decrease in the filter gap in the flow direction.
  • the width of the contact surface of these spacers increases inwardly while the top of the annular disc drops inwardly.
  • the narrow side of the approximately triangular spacer may be the center of the ring or turned away.
  • the width of the contact surface 11 of the spacers is measured in the radial direction, as the largest extent in the radial direction.
  • the width of the contact surface of the spacers is less than or equal to the radial width of the annular discs and is preferably at least 60% of the radial annular width.
  • the width of the spacers may be slightly shortened at the outer circumference of the annular discs for the introduction of measuring reference surfaces 33, for example by about 0.3 mm (see FIGS. 6e and 8e ).
  • the measurement reference surfaces are used for simplified measurement of the filter width, in particular the automated measurement.
  • the length of the contact surface 11 of the spacers is measured in the circumferential direction, as the largest extent in the circumferential direction.
  • the length of the contact surface of the spacers is preferably between 1 mm and 12 mm and particularly preferably between 2 mm and 5 mm. These lengths have proven particularly useful in compression tests and in the manufacture of annular discs.
  • the contact surface 11 of the individual spacers is preferably between 4 and 60 mm 2 , more preferably between 10 and 35 mm 2 .
  • At least three spacers 10 are evenly distributed over the circumference of the annular discs.
  • the number of spacers may be even or odd.
  • the fluid pressure acting on the flow in the filter gap also stresses the annular discs on bending.
  • the pressure resistance determining field width or span is the distance of adjacent spacers. The fewer spacers are placed on the annular discs, the lower the pressure resistance of the separator.
  • the free filter area decreases undesirably as the number of spacers increases, the pressure resistance of the filter system increases as the field width or span decreases.
  • more than three spacers are provided, more preferably at least 6, more preferably at least 10 and most preferably at least 15.
  • the number of spacers to be selected depends on the application or the expected pressure conditions and depending on the mechanical properties of the material used for the annular discs, the number of spacers to be selected. The higher the pressures to be expected during operation, the more spacers are to be provided structurally. The larger the annular discs are, the more spacers are usually structurally provided.
  • 16 spacers are provided at an outer diameter of 115 mm (for basic tube outer diameter of 31 ⁇ 2 inches)
  • 18 spacers may for example be provided and with an outside diameter of 168 mm (for base tube outside diameter of 51 ⁇ 2 inches), for example, 24 spacers can be provided.
  • the distance between the spacers is measured in the circumferential direction as a distance between the centers of the contact surfaces of the spacers along the inner diameter.
  • the distance between the spacers is preferably in the range of 8 to 50 mm, more preferably between 10 and 30 and more preferably between 15 and 25 mm.
  • the distance between the spacers affects the resistance to internal and external pressure loads that can occur during the test for internal and external pressure resistance according to ISO 17824 as well as under operating conditions. The smaller the distance of the spacers, the higher are the internal and external pressures that the separator can withstand before the filter effect is lost.
  • the number of spacers for the different sizes of the annular discs can be derived.
  • the annular discs may be stacked in random and random orientation without compromising the function of the separator. It is therefore not necessary that the spacers of the annular discs are each positioned exactly aligned one above the other. This possibility of random and random orientation in the stacking facilitates the assembly of the separation device considerably and also means that the production costs are lower than in a stacking with exactly one above the other oriented spacers. However, it is also possible to position the spacers in the ring stack one above the other, as in FIG Figure 7f shown.
  • the brittle-hard material of the annular discs is selected from oxidic and non-oxidic ceramic materials, mixed ceramics from these materials, ceramic materials with the addition of secondary phases, mixed materials with shares of ceramic or metallic hard materials and metallic binder phase, powder metallurgy materials with in-situ formed hard material phases and long - and / or short fiber reinforced ceramic materials.
  • oxidic ceramic materials are materials based on Al 2 O 3 , ZrO 2 , mullite, spinel and mixed oxides.
  • non-oxidic ceramic materials are SiC, B 4 C, TiB 2 and Si 3 N 4 .
  • Ceramic hard materials are, for example, carbides and borides.
  • mixed materials with metallic binder phase are WC-Co, TiC-Fe and TiB 2 -FeNiCr.
  • in-situ formed hard material phases are chromium carbides.
  • An example of fiber reinforced ceramics is C / SiC.
  • the material group of the fiber-reinforced ceramic materials has the advantage that it leads due to their higher strength compared to monolithic ceramic to even higher internal and external pressure resistance of the separation devices.
  • the above-mentioned materials are characterized by being harder than the typically occurring solid particles such as sand and rock particles, ie the HV (Vickers) or HRC (Rockwell Method C) hardness values of these materials are above the corresponding values of the surrounding rock.
  • Suitable materials for the annular disks of the separating device according to the invention have HV hardness values greater than 15 GPa, preferably greater than 23 GPa.
  • brittle hard All of these materials are characterized by the fact that they have a greater brittleness than typical unhardened steel alloys. In this sense, these materials are referred to herein as "brittle hard”.
  • Suitable materials for the annular disks of the separating device according to the invention have moduli of elasticity greater than 200 GPa, preferably greater than 350 GPa.
  • materials with a density of at least 90%, more preferably at least 95%, of the theoretical density are used in order to achieve the highest possible hardness values and high abrasion and erosion resistance.
  • the sintered silicon carbide (SSiC) or boron carbide is preferably used as the brittle-hard material. These materials are not only abrasion resistant, but also corrosion resistant to the treatment fluids commonly used for flushing the separator and stimulating the well, such as acids, such as HCl, alkalis, such as NaOH, or even water vapor.
  • SSiC materials with a fine-grained microstructure such as those sold under the name 3M TM silicon carbide type F and 3M TM silicon carbide type F plus by ESK Ceramics GmbH & Co. KG.
  • coarse-grained SSiC materials for example with a bimodal microstructure, wherein preferably 50 to 90% by volume of the particle size distribution consists of prismatic platelet-shaped SiC crystallites having a length of 100 to 1500 ⁇ m and 10 to 50% by volume prismatic, platelet-shaped SiC crystallites of a length of 5 to less than 100 ⁇ m (3M TM silicon carbide type C from ESK Ceramics GmbH & Co. KG).
  • liquid phase sintered silicon carbide can also be used as the material for the annular disks (LPS-SiC).
  • LPS-SiC liquid phase sintered silicon carbide
  • An example of such a material is 3M TM silicon carbide type T from ESK Ceramics GmbH & Co. KG.
  • LPS-SiC a mixture of silicon carbide and metal oxides is used as the starting powder.
  • LPS-SiC has higher flexural strength and higher toughness, measured as Klc value, than single-phase sintered silicon carbide (SSiC).
  • the annular disks of the separating device according to the invention are produced by the methods customary in technical ceramics or powder metallurgy, that is to say preferably by die pressing of ready-to-use starting powders and subsequent sintering.
  • the annular discs are molded, debindered and then sintered to densities> 90% of theoretical density according to the principles of "near-net shape forming" on mechanical or hydraulic presses.
  • the annular discs For high demands on the size distribution of the filter width, d. H. if an accurate average and small tolerances of the filter width are required, the annular discs must be subjected to two-sided plan machining on their top and bottom surfaces. Preferred methods for two-sided plan processing are lapping, flat honing and grinding. The hard machining ensures that the annular discs have a sufficiently large surface contact with each other and any point load is avoided, which is of the utmost importance for high pressure resistance of the mounted separator.
  • the heights of the flat spacers can be adjusted to accuracies in the micrometer range.
  • the hard machining also makes it possible to set customer-specific desired filter openings from sintered parts with unit height of the spacers.
  • the flatness of the rings on both sides should be better than 30 microns, preferably better than 15 microns and more preferably better than 5 microns.
  • the perforated tube 1 (see FIGS. 1 . 3 a - 3 b, 4 a - 4 b and 5 a - 5 b), which is located inside the ring stack and on which the annular discs are stacked, also referred to as the base tube.
  • the base tube is perforated in the area of the ring stack, ie provided with holes, outside the area of the ring pile it is not perforated.
  • the perforation 18 serves to direct the filtered medium, ie the freed of the solid particles media stream, such as gas, oil or mixtures thereof, into the interior of the base tube, from where it can be conveyed off or pumped out.
  • the base tube ensures the mechanical stability and the cohesion of the overall construction.
  • the base pipe used can be tubes used in the oil and gas industry for wire wrap filters and metal mesh screens.
  • the perforation is applied according to industry standard schemes, for example, 30 holes of 9.52 mm diameter can be placed on a 0.3048 m (one foot) base tube length.
  • the base pipe is made of a metallic material, usually steel, for example steel L80.
  • Steel L80 refers to a steel having a yield strength of 80,000 psi (corresponding to approximately 550 MPa).
  • steel L80 it is also possible to use steels which are referred to in the oil and gas industry as J55, N80, C90, T95, P110 and L80Cr13 (see Drilling Data Handbook, 8th Edition, IFP Publications, Editions Technip, Paris, France ). It is also possible to use other steels, in particular corrosion-resistant alloyed and high-alloy steels, as the material for the base tube.
  • base tubes made of nickel-based alloys can also be used.
  • aluminum materials as base tube material to save weight.
  • base tubes made of titanium or titanium alloys can be used.
  • the inner diameter of the annular discs must be greater than the outer diameter of the base tube. This is necessary because of the differences in the thermal expansion between the metallic base tube and the annular discs of the brittle-hard material and fluidic reasons. As low has been found that the inner diameter of the annular discs at least 0.5 mm and at most 10 mm larger than the outer diameter of the base tube. Preferably, the Inner diameter of the annular discs at least 1.5 mm and at most 5 mm larger than the outer diameter of the base tube.
  • the base tube 1 On the outer circumferential surface 21 of the base tube 1 at least three bands 15 are mounted axially parallel at a uniform distance (see Figures 10 and 11 ). On these bands, the annular discs 8 are pushed during assembly, whereby a centering of the annular discs is achieved on the base tube. Due to their function, these bands can also be referred to as centering belts.
  • the centering belts are elastically deformable, especially in the radial direction. By the centering and the thermal expansion differences between the base tube 1 and the ring stack 7 can be compensated in the radial direction. In addition, production-related diameter tolerances of the base tube and the annular discs can be compensated by the centering.
  • the centering of the ring stack on the base tube also serves to set a uniformly wide annular gap between the base tube and ring stack. This ensures that the filtrate can flow evenly through several perforation holes in the base pipe.
  • the length of the centering bands corresponds at least to the length of the ring stack, since thus all annular discs of the ring stack including the first and last annular disc are centered.
  • the centering belts can be made flat or profiled.
  • the profiling can be, for example, a bulging deformation inwards or outwards.
  • FIG. 10 is a cross-sectional view of a separator according to the invention with a flat design of the centering belts 15 shown
  • FIG. 11 shows a cross-sectional view of a separator according to the invention with centering bands 15, which are executed with a curvature, wherein the convex side of the curved band is oriented inwards.
  • the material for the centering is preferably to be chosen so that it does not corrode under operating conditions and it must be resistant to oil, water and temperature be.
  • a material for the centering metal or plastic is suitable, preferably metallic alloys based on iron, nickel and cobalt, more preferably steel, more preferably spring band steel.
  • spring strip steel with the material number 1.4310, design spring-hard can be used as material for the centering belts, available for example from COBRA Bandstahl GmbH, D-63607 Wamba.
  • the width of the centering bands may be, for example, 16 mm and the thickness 0.18 mm.
  • the centering straps can be fastened to the base tube by means of screws, rivets, notched nails or gluing or with another common fastening method. If steel is used as material for the centering belts, the belts can also be attached to the base pipe by means of welding or spot welding.
  • the centering can be installed in one or more layers to compensate for diameter tolerances of the base tube and / or the annular discs.
  • the thickness and width of the centering straps should be selected so that the annular discs with "sliding fit" on the base tube can be moved axially. This means that the annular discs do not move axially in their vertical position under their own weight. This is usually the case when the force for moving the annular discs on the base tube in the horizontal direction, ie without the influence of gravity, between 0.1 N and 10 N, preferably between 0.5 N and 5 N, is located ,
  • an end cap 5, 6 (see FIGS. 1 . 3 a - 3 b, 4 a - 4 b and 5 a - 5 b).
  • the end caps are firmly connected to the base tube.
  • the end caps are made of metal, usually steel, and preferably of the same material as the base tube.
  • the end caps can be attached to the base tube by welding, clamps, rivets or screws. During assembly, the end caps are pushed onto the base tube after the ring stack and then fastened to the base tube.
  • the end caps are secured by welding (see the weld 20). If the end caps are fastened by means of clamping connections, constructive friction-increasing measures are preferably taken.
  • friction-increasing measures for example friction-increasing coatings or surface structuring can be used.
  • the friction-increasing coating can be carried out, for example, as a chemical nickel layer with embedded hard material particles, preferably diamond particles.
  • the layer thickness of the nickel layer is, for example, 10 - 25 microns, the average size of the hard material particles is for example 20 - 50 microns.
  • the friction-increasing surface structuring can be applied for example as laser structuring.
  • the separating device according to the invention has no yielding-elastic construction elements such as springs, rubber washers or other elastic elements which cause a bias.
  • the ring stack of the separator is not tensioned by compression springs, but fixed on the base tube by means of the end caps, without the ring stack undergoes a significant bias. By dispensing with the compression springs, it can not lead to tilting of the annular discs.
  • the preload in the ring stack in the axial direction must be so large that due to the production is not quite flat annular discs of the ring stack are charged so that all spacers have contact with the flat surface of the adjacent annular disc.
  • the bias in the ring stack in the axial direction is in the temperature range of 10 ° C to 200 ° C preferably at most 10 MPa, more preferably at most 5 MPa, more preferably at most 2 MPa, based on the axial projection surface of the annular discs.
  • the caused by fluid pressure differences in the operation of the separator displacement of the annular discs in the ring stack is in the temperature range of 10 ° C to 200 ° C preferably not more than 0.5 percent in the axial direction, based on the length of the ring stack.
  • the separation device is preferably of a freely permeable tubular protective cage 4 (see FIG. 1 ) surround.
  • This protective cage can, for example, as a coarse mesh screen and preferably made Perforated sheet to be executed.
  • the protective cage is preferably made of a metallic material, more preferably of steel, more preferably of corrosion-resistant steel.
  • the protective cage may be made of the same material from which the base tube is made.
  • the protective cage is held on both sides by the end caps, it can also be firmly connected to the end caps. This fixation is possible for example by gluing, screwing or pinning, preferably the protective cage is welded to the end caps after assembly.
  • the inner diameter of the protective cage must be greater than the outer diameter of the annular discs. This is required for fluidic reasons. As low has been found that the inner diameter of the protective cage is at least 0.5 mm and at most 15 mm larger than the outer diameter of the annular discs. Preferably, the inner diameter of the protective cage is at least 1.5 mm and at most 5 mm larger than the outer diameter of the annular discs.
  • the length of the ring stack of the separation device according to the invention is between 300 and 2,000 mm, preferably between 1,300 and 1,700 mm.
  • the application also requires separators with lengths of more than 2,000 mm. Larger lengths of the separator can be realized by mounting a plurality of ring stacks, each top and bottom with a sealing bushing and an end cap, onto a common, continuous base tube. Alternatively, a plurality of base tubes, each with a ring stack, which is completed at the top and bottom each with an end cap, are screwed together.
  • FIG. 2 a shows the view of a separating device according to the invention with an intermediate element
  • FIG. 2b shows the view of a separating device according to the invention with two intermediate elements.
  • the embodiment with the intermediate element also has the advantage that it is space-saving, which allows more filter surface to accommodate a given length of the base tube.
  • An intermediate element is fixed on the base tube in the radial and axial directions, for example by welding, clamping, riveting or screwing.
  • friction-increasing measures for example friction-increasing coatings or surface structuring can be used.
  • the friction-increasing coating can be carried out, for example, as a chemical nickel layer with embedded hard material particles, preferably diamond particles.
  • the layer thickness of the nickel layer is, for example, 10 - 25 microns, the average size of the hard material particles is for example 20 - 50 microns.
  • the friction-increasing surface structuring can be applied for example as laser structuring.
  • the intermediate elements are preferably made of metal, more preferably of steel, more preferably of the same material as the base tube.
  • a sealing bushing 16, 17 At the upper and lower end of the ring stack 7 is preferably in each case a sealing bushing 16, 17 (see Figures 3 a - 3 b, 4 a - 4 b and 5 a - 5 b).
  • the sealing bush has the task of the penetration of pressurized liquids and / or gases, such as test liquid in the test for external pressure resistance (collapse pressure test) in constructive cavities, such as chamfers and gaps, between the end cap and the base tube or other construction elements such as the compensation socket 22, 23 (see Figures 3 a - 3 b) or the double wall compensator 24, 25 (see FIGS. 4 a - 4 b).
  • the pressurized liquid or the pressurized gas via the hydraulically active annular surface of the uppermost annular disc or over the axial surface of the compensating sleeve 22, 23 or the double wall compensator 24, 25 exert a strong axial force on the ring stack, which Breakage of the annular discs could result.
  • an O-ring 19 is inserted in the sealing bushing.
  • On the inner peripheral surface of the sealing bush also an O-ring can be introduced. The sealing bushing with the O-ring seals prevents pressurized fluid and / or gas from entering areas of the separator that are not related to the filter function.
  • the sealing bushes 16, 17 are pushed during assembly to the base tube 1, then to the ring stack 7. Finally, the end cap is pushed over the O-ring 19 of the sealing bush, so that the penetration of liquid and / or gas in areas of the Pressure side is prevented.
  • the wall thickness of the sealing bushes 16, 17 is on the side on which they are in contact with the ring stack, preferably equal to the axial wall thickness, so the radial ring width, the brittle discs.
  • a wear and corrosion resistant material is used, such as a metallic or ceramic material or carbide.
  • the preferred material for the sealing bushing is steel. Particularly preferably, the same material is used for the sealing bush, as used in the base pipe.
  • the metallic materials used to produce the perforated base tube such as steel L80, have a higher thermal expansion than the brittle-hard material of the annular discs, such as, for example, the silicon carbide ceramic which is preferably used.
  • the coefficient of expansion is about 10.5 * 10 -6 / K in the temperature range of 10 ° C to 200 ° C
  • the expansion coefficient of sintered single-phase silicon carbide (SSiC) is 2.8 * 10 -6 / K in the temperature range of 10 ° C to 200 ° C.
  • the separator could only be used at temperatures slightly different from the mentioned 20 ° C. If the separator were used at higher temperatures, for example, 100 ° C, the base tube would expand more axially than the ring stack. As a result, the contact between the rings would no longer be free of play, but rather the distance between the rings could increase, which would change the filter width in an undesired manner.
  • the base tube Upon cooling of the system, such as during transport or storage in a cold environment, the base tube would contract more than the ring stack, which could lead to high compressive stresses in the annular discs and possibly their breakage.
  • FIG. 12 shows different views of the compensation socket ( Fig. 12 a 3D view, Fig. 12b At sight, Fig. 12c Cross-sectional view along in Fig. 12b with "12 c" designated cutting line).
  • the compensation bushing For the production of the compensation bushing are pressure-resistant materials that are resistant to oil, water and steam and do not swell or only slightly. In addition, the materials must be able to be used at high temperatures (up to approx. 200 ° C) and have a pressure resistance of> 1 MPa.
  • the coefficient of thermal expansion (CTE) of the material used for the compensating bush should be significantly higher than the coefficient of thermal expansion of the material of the brittle-hard annular disks,
  • the silicon carbide preferably used WAK SiC about 2.8 * 10 -6 / K
  • the coefficient of thermal expansion of the metallic base pipe WAK metals to about 23 * 10 -6 / K
  • the coefficient of thermal expansion of the material of the compensation bushing is preferably at least 25 ⁇ 10 -6 / K, more preferably at least 80 ⁇ 10 -6 / K, particularly preferably at least 100 ⁇ 10 -6 / K, in the temperature range from 10 ° to 200 ° C. ,
  • PTFE polytetrafluoroethylene
  • PTFE polytetrafluoroethylene
  • the height of the bushing is primarily calculated.
  • the inner diameter of the compensation bushing preferably corresponds to the outer diameter of the base pipe, the outer diameter of the compensation bushing preferably corresponds to the outer diameter of the annular disks.
  • the height of each socket is halved (H K / 2).
  • the coefficients of expansion of the materials used for the base tube, the ring stack and the compensation bushing are usually only average values and the coefficient of thermal expansion can be batch-dependent, since it depends on, for example, grain size, texture, heat treatment and variations in the alloy composition it is necessary to determine the coefficients of thermal expansion of the materials actually used by dilatometer measurements before designing the compensating bushing.
  • the compensating bushing is sufficiently stiff not to be plastically deformed by the axial forces caused by pressure differences that occur during operation of the separator.
  • the separator retains the predetermined filter width and thus its full filter effect even with large pressure differences. Even with inhomogeneous pressurization, for example, in only one segment of the circumference of the ring stack, it can not lead to a tilting of the rings.
  • the compensating bushing has a certain amount of flexibility so that the separating device can make bends when it is introduced into the borehole.
  • the material of the compensation bushing has an E-modulus of at most 15,000 MPa, more preferably of at most 2,000 MPa.
  • each a sealing bushing 16, 17 is located at both ends of the ring stack, between the compensation bushing and the ring stack, each a sealing bushing 16, 17 (see Figures 3 a - 3 b).
  • an O-ring 19 is inserted in the sealing bushing.
  • the sealing bush has, like described above, the task of the penetration of pressurized liquids and / or gases into constructive cavities, such as chamfers and gaps, between the end cap and the base tube and the compensation sleeve 22, 23 (see Figures 3 a - 3 b).
  • the sealing bushing 16, 17 assumes in the embodiment with the compensation bushing the additional function of balancing the greatly different resiliencies of the compensation bushing 22, 23 and the brittle-hard annular disks 8, ie the function of the load distribution.
  • the sealing bush mitigates the stiffness jump between the compensating bush made of a soft low-modulus material and the brittle-hard material of the high modulus annular disks.
  • the modulus of elasticity of PTFE is about 700 MPa and that of sintered silicon carbide (SSiC) about 440,000 MPa.
  • the compliance of the compensation bushing is much higher than that of the ring stack due to the large difference in the modulus of elasticity.
  • the compensation bushing 22, 23 is pushed onto the base tube during assembly of the separating device after the ring stack and the sealing bushing. Thereafter, the end cap is pushed over the compensation bushing and fastened to the base tube.
  • a compensation element 24, 25 to compensate for the different thermal change in length of base tube 1 and ring stack. 7 .
  • a compensation bush made of a material having a high coefficient of thermal expansion, but a filled with a liquid double-walled container.
  • the liquid container is tubular.
  • the outer walls of the double-walled liquid container are corrugated in the axial direction and therefore designed so that the high thermal volume expansion of a liquid is diverted into a linear axial extent of the liquid container, so that the liquid container has a high thermal expansion.
  • the construction of a liquid container is shown, which fulfills this function.
  • the in the Figures 13 a - 13 c shown liquid container has the form of a double-walled corrugated tube sleeve ( Fig. 13 a 3D view, Fig. 13b At sight, Fig. 13c Cross-sectional view along in Fig. 13b with "13 c" designated cutting line).
  • the liquid container Due to its double-walled shape, the liquid container is called a double wall compensator (DWK).
  • DWK double wall compensator
  • the height H of the double wall compensator is designed so that it compensates the difference in length due to temperature expansion between the ring stack and the base tube with the aim to keep the filter width constant even when heating the separator, ie to maintain the contact of the annular discs.
  • a suitable liquid for filling the double wall compensator is a mineral oil of high thermal expansion, such as diesel oil, whose presence in oil and gas wells is not a problem.
  • the double wall compensator has the additional advantage over the compensating bush of the embodiment described above in that it has good angular mobility and therefore improves the flexibility of the entire separating device.
  • a double wall compensator separator can pass a radius of curvature downhole of approximately 43.7m, corresponding to a bend of 40 ° / 100ft or 40 ° /30.48m, without damage to the separator, which is sometimes required in oil and gas wells becomes.
  • bends of 20 ° / 100 ft and 20 ° / 30.48 m are possible, corresponding to a radius of curvature of 87.3 m.
  • the double wall compensator is sufficiently rigid so as not to be affected by the axial forces caused by pressure differences occurring during operation of the separator. to be plastically deformed.
  • the separator retains the predetermined filter width and thus its full filter effect even with large pressure differences. Even with inhomogeneous pressurization, for example, in only one segment of the circumference of the ring stack, it can not lead to a tilting of the rings.
  • the double wall compensator has a certain flexibility so that the separating device can enter bends when it is introduced into the borehole.
  • the double wall compensator 24, 25 is located at both ends of the ring stack, between the double wall compensator and the ring stack, preferably in each case a sealing bushing 16, 17 (see FIGS. 4 a - 4 b).
  • a sealing bushing 16, 17 On its outer peripheral surface, an O-ring 19 is inserted in the sealing bushing.
  • the sealing bush has, as described above, the task to prevent the ingress of pressurized liquids and / or gases into constructive cavities, such as chamfers and gaps, between the end cap and the base tube and the double wall compensator 24, 25.
  • the double wall compensator is pushed during assembly of the separator after the ring stack and the sealing bushing on the base tube. Thereafter, the end cap is pushed over the liquid container and fixed on the base tube.
  • FIGS. 5 a and 5 b show the cross-sectional view of a separating device according to the invention according to a third and fourth preferred embodiment.
  • a metallic material whose thermal expansion coefficient comes close to that of the annular discs.
  • the base tube is made of a material whose thermal expansion coefficient in the temperature range of 10 ° C to 200 ° C by at most 10%, preferably at most 5% deviates from the coefficient of thermal expansion of the material of the ring stack in the temperature range of 10 ° C to 200 ° C.
  • Such a material may be, for example, the iron-nickel alloy Fe36Ni with the material number 1.3912, which is known under the trade name Invar.
  • Other trade names are Nilo alloy 36, Nilvar, NS 36, Permalloy D, Radio metal 36, Vacodil 36 and Pernifer 36.
  • the thermal expansion coefficient of this material is 2.6 * 10 -6 / K and fits well in the temperature range of 10 to 200 ° C to that Expansion coefficient of the material of the annular discs, for example, to that of the preferably used silicon carbide ceramics.
  • the thermal expansion coefficient of this material is adjustable via the alloy composition and can be adapted to the material used for the ring stack.
  • the thermal expansion coefficient of the material of the base tube is adapted to that of the material of the ring stack
  • no further measures for length compensation due to different thermal expansion coefficients of the base tube and ring stack are required.
  • a separate compensation element such as the compensation bush or the double wall compensator.
  • additional compensation elements located at the top and bottom of the ring stack preferably sealing bushes 16, 17 (see Figures 5 a - 5 b).
  • an O-ring 19 is inserted in the sealing bushing.
  • the sealing bushes 16, 17 are pushed onto the base tube 1 after the ring stack 7, then end caps 5, 6 are pushed onto the base tube 1 and fastened to the base tube.
  • the separating device according to the invention according to the third embodiment with a ring stack 7 made of silicon carbide ceramic and a base tube 1 made of Pernifer 36.
  • a separating device constructed in this way in a climate chamber have shown that in the range from 10 ° C. to 200 ° C. neither undesired filter gap widening occurs between the ceramic rings nor the ceramic rings break due to excessive compressive stresses in the rings.
  • a ceramic material based on zirconium dioxide (ZrO 2 ) is used as the material for the annular discs.
  • the thermal expansion coefficient of zirconia ceramics is similar to the coefficient of thermal expansion of the steel grades commonly used for the base tube.
  • the thermal expansion coefficient of the zirconia ceramic in the temperature range of 10 ° C to 200 ° C deviates by at most 10%, more preferably at most 5% from the coefficient of thermal expansion of the material of the base tube in the temperature range of 10 ° C to 200 ° C.
  • the ring stack is constructed from annular discs which are made of different brittle-hard materials.
  • annular discs of silicon carbide and zirconia ceramic may be stacked alternately.
  • the number of annular discs of the different materials is chosen so that the ring stack as a whole has a thermal expansion corresponding to that of the base tube.
  • the material used for the base tube is preferably a material adapted to the thermal expansion coefficient, for example an iron-nickel alloy.
  • inventive separation device in the upper and / or in the lower compensation bushing 22, 23 mounted over the circumference uniformly distributed holes in the coil springs 27 are used (see Figures 14 a - 14 c and 15 a - 15 c).
  • the coil springs are pressed against the sealing bushing 16, 17.
  • the holes can be designed as blind holes (see Figure block 14; Fig. 14 a 3D view, Fig. 14b At sight, Fig. 14c Cross-sectional view along in Fig. 14b with "14 c" designated cutting line) or as through holes (see Figure block 15; Fig. 15 a 3D view, Fig. 15b At sight, Fig. 15c Cross-sectional view along in Fig. 15b with "15 c" cut line).
  • the spring constant of the coil springs can be for example 10 N / mm.
  • the coil springs are preloaded by compressing them to the depth of the bore so that the coil springs are flush with the plan side of the compensating bushing.
  • the depth of the holes is chosen so that the coil springs in the prestressed state, a total force of at least 500 N.
  • a metal disk of thickness ⁇ 2 mm is inserted, the thickness of which is added to the depth of the hole.
  • the ring stack is built up from two differently shaped annular disks which are stacked alternately.
  • the first shape of the annular discs has in this case spacers with a flat contact surface on both sides, the second form of the annular discs are simple two-sided planar rings with the same inner and outer diameter as in the first form.
  • the top and bottom of the second shape of the annular discs is smooth and flat, formed at right angles to the disc axis.
  • the spacers on the first shape of the annular discs are each formed identically on the top and bottom.
  • the number, type, arrangement and dimensions of the spacers on the annular discs of the first shape are chosen so that they correspond to the number, type, arrangement and dimensions in one of the embodiments listed above.
  • the embodiment of the top and bottom of the annular discs of the first shape corresponds in the areas between the spacers of the embodiment of the top of the annular discs in one of the embodiments listed above, ie the top and bottom of the annular discs of the first shape is in the areas preferably sloping inwardly or outwardly between the spacers.
  • the top and bottom of the annular discs in the areas between the spacers sloping inwards.
  • the lowermost and the uppermost of the annular disks of the annular stack are preferably made of the second form, ie there are planar rings without spacers on both sides.
  • the inventive separation device is shown with the ring stack 7, in the alternative embodiment of the separation device is in the Figures 3 a - 3 b, 4 a - 4 b and 5 a - 5 b of the ring stack 7 replaced by the ring stack 32. All other construction elements remain unchanged.
  • FIG. 16 Figure a shows a plan view of an annular disc 28 with 15 spacers on the top and bottom, stacked in the ring stack 32 as each second annular disc, alternating with the annular discs 31.
  • FIG. 16b shows a cross-sectional view along in FIG. 16 a with "16 b" designated cutting line
  • the Figures 16c - 16e show enlarged sections of the cross-sectional view of FIG. 16 b.
  • FIG. 16f shows a 3D representation along the in FIG. 16 a cut line labeled "16 f”
  • FIG. 16g shows a 3D view of the annular disc.
  • FIG. 7 a shows a top view of the ring stack
  • FIG. 7b shows a cross-sectional view along in FIG FIG. 7 a with "7 b" designated cutting line.
  • the FIGS. 7c and 7d show enlarged sections of the cross-sectional view of FIG. 7 b.
  • Figure 7e shows a 3D view of the ring stack
  • Figure 7f shows a 3D representation along the in FIG. 7 a with "7 f" designated cutting line.
  • the further details of this embodiment correspond to those of the previously described embodiments, such as the dimensions of the brittle annular disks 28, 31, the embodiment of the base pipe first
  • the dimensions, configuration, number and arrangement of the spacers 10 correspond to the dimensions, the configuration, number and arrangement of the spacers in one of the embodiments listed above
  • the configuration of the top and bottom 29, 30 of the first form of the annular discs 28 with the spacers on the top and bottom corresponds in the areas between the spacers (see FIG.
  • the design of the top of the annular discs in the embodiment with spacers only on the top, ie the top and bottom 29, 30 of the first form of the annular discs 28 with the spacers on the top and bottom is sloping inwards or outwards, preferably sloping inwards.
  • the annular discs can be stacked in random and random orientation;
  • the spacers in the ring stack in each case to position one above the other, as in FIG. 17f shown.
  • intermediate elements can be used.
  • compensation elements can be used to compensate for the different thermal changes in length of the base tube and ring stack, such as compensating bushes or double wall compensators at the top and / or bottom of the ring stack.
  • this alternative embodiment is comparable to the previously described embodiments, but has advantages in the production of the annular discs.
  • the annular discs For the two-sided Läppplanbearbeitung the annular discs, it is advantageous if the ablated surfaces at the top and bottom are the same size, since then the Läppabtrag on both sides is the same and the height of the flat spacers is easier to control precisely. If the surfaces to be removed differ at the top and bottom, an asymmetrical and thus more difficult material removal results. The same applies to the two-sided plan annular discs.
  • This ring shape is easy to work with and any thickness tolerances of the annular discs have no effect on the absolute size of the filter width. In this embodiment, the separator can thus be set even tighter tolerances in the filter width.
  • the separation device according to the invention is used in production wells in oil and / or gas reservoirs for the separation of solid particles from the volume flows of crude oil and / or natural gas.
  • the separation device can also be used for other filtration processes for the separation of solid particles from liquids and / or gases outside of production wells, where a high abrasion resistance and long life of the separation device are required, such as for filter processes in mobile and fixed storage facilities for liquids and / or gases or for filtering processes in natural waters such as in the filtering of seawater.
  • the separation device according to the invention is particularly suitable for the separation of solid particles from liquids or gases, especially from oil, natural gas and water, in production wells in which high and highest flow rates and delivery volumes and thus high pressure differences between inflow and outflow of the separator occur.
  • a separating device according to the invention according to the Figures 3 a - 3 b is inserted into a borehole.
  • Temperature 150 ° C.
  • the material used for the base pipe is steel L80.
  • the material used for the ring stack is sintered silicon carbide (SSiC; 3M TM silicon carbide type F, ESK Ceramics GmbH & Co. KG).
  • SSiC sintered silicon carbide
  • 3M TM silicon carbide type F ESK Ceramics GmbH & Co. KG
  • a compensation bush made of PTFE (polytetrafluoroethylene) is used at one or both ends of the ring stack.
  • the PTFE compensating bushing prevents gaps between the annular disks, which are larger than the desired filter width, from forming at the higher temperatures at the place of use.
  • the height of the ring stack is 1000 mm.
  • the thermal expansion coefficient ⁇ steel of the steel used for the base pipe L80 is 10.5 ⁇ 10 -6 / K
  • the thermal expansion coefficient ⁇ SSiC of the SSiC material used for the ring stack is 2.8 * 10 -6 / K
  • the compensating sleeve made of PTFE must have a length of 1.00 mm.
  • the thermal expansion coefficient ⁇ of PTFE is 125 * 10 -6 / K.
  • a PTFE compensation bush, which expands by 1.00 mm at ⁇ T 130 K, must therefore have a length H K of 61.54 mm.
  • the length halves to 30.77 mm.
  • a separating device according to the invention according to the Figures 3 a - 3 b is used at a temperature of 200 ° C.
  • the height of the ring stack is 1500 mm.
  • the material used for the base pipe is steel 1.4563 (Incoloy® Alloy 028).
  • the material used for the ring stack is sintered silicon carbide (SSiC; 3M TM silicon carbide type F, ESK Ceramics GmbH & Co. KG).
  • the thermal expansion coefficient ⁇ steel of the material used for the base pipe is 15.2 * 10 -6 / K
  • the thermal expansion coefficient ⁇ SSiC of the SSiC material used for the ring stack is 2.8 * 10 -6 / K
  • the difference between the length expansion of ring stack and base tube is thus 3.34 mm.
  • the compensating sleeve made of PTFE must have a length of 3.34 mm.
  • the coefficient of thermal expansion ⁇ of PTFE is 125 * 10 -6 / K.
  • a PTFE compensation bush, which expands by 3.34 mm at ⁇ T 180 K, must thus have a length H K of 148.44 mm.
  • annular disks of sintered silicon carbide (SSiC, 3M TM silicon carbide type F, ESK Ceramics GmbH & Co. KG) are stacked on top of each other and subjected them in a universal testing machine ZWICK 1474 TestXpert II a pressure ramp until the breakage of one or more rings occurs or the maximum force, ie the performance limit of the testing machine, of 100 kN is reached.
  • annular discs having spherical section spacers are employed. The results are shown in Table 1. ⁇ u> Table 1: ⁇ / u> Example no.
  • the high-pressure chamber has an inner diameter of 80 mm and a usable length of 500 mm.
  • the liquid pressure is applied by a compressed air piston pump (type GRACO X-treme 70, manufactured by Graco Inc., Russell J. Gray Technical Center, 88-11th Avenue Northeast, Minneapolis, Minnesota 55413, USA) which is 500 bar (corresponding to 50 MPa resp 7250 psi).
  • a compressed air piston pump type GRACO X-treme 70, manufactured by Graco Inc., Russell J. Gray Technical Center, 88-11th Avenue Northeast, Minneapolis, Minnesota 55413, USA
  • the pressure transfer medium used is a viscous mixture of methyl cellulose, water and limestone powder of different particle sizes in accordance with ISO 17824 Annex A.4 (fluid loss control pill).
  • the task of the pressure transfer medium is to block the separating gaps (filter gaps) and seal them so that a pressure difference can be built up.
  • the outer diameter of the annular discs of the separators used is 58 mm, the inner diameter is 42 mm and the usable length is 350 mm.
  • the usable length corresponds to the height of the ring stack.
  • the filter width is 250 ⁇ m.
  • the material of the annular discs is a single-phase sintered silicon carbide with a density> 3.10 g / cm 3 (SSiC; 3M TM silicon carbide type F, manufacturer: ESK Ceramics GmbH & Co. KG).
  • the base pipe of the separator is made of steel 1.4571.
  • the outer diameter of the base tube is 38 mm.
  • Examples Nos. 9 and 12 are according to the invention, examples Nos. 10 and 11, and 13 and 14 are reference examples.
  • annular discs For the inventive examples Nos. 9 and 12, a separation device according to the Figures 5 a - 5 b used.
  • the execution of the annular discs corresponds to the FIGS. 8 a - 8 g, but instead of the 24 spacers shown here, the annular disc has only 8 evenly spaced spacers.
  • the annular discs On the inner and outer circumferential surfaces, the annular discs have no grooves or recesses.
  • the ring stack is not clamped on both sides with compression springs axially, but attached on both sides with one end cap on the base tube.
  • the preload in the ring stack in the axial direction is ⁇ 2 MPa, based on the axially projected surface of the annular discs.
  • a separator is used in which the annular discs with 3 spherical section spacers according to FIG. 2 of the WO 2011/120539 A1 are provided. On the inner peripheral surface of the annular discs are 3 evenly distributed over the circumference of the grooves.
  • the ring stack is axially braced on both sides with compression springs and secured on both sides with one end cap on the base tube.
  • a separator is used, in which the annular discs with 3 spherical section spacers according to FIG. 2 of the WO 2011/120539 A1 are provided. On the inner peripheral surface of the annular discs are 3 evenly distributed over the circumference of the grooves.
  • the ring stack is not clamped with compression springs, but fixed on both sides with one end cap. Between the ring stack and the end caps is located on both sides of the ring stack each have a sealing bush made of steel, as in FIG. 5 is shown.
  • Example No. 12 the maximum pressure of the testing device was reached without the separator failing.
  • test results show the significantly higher compressive strength of the separating device according to the invention over the embodiment with spherical segment-shaped spacers on the annular discs and against the tension of the ring stack with compression springs.
  • a larger high pressure chamber is built which is larger than that used for Examples Nos. 9 to 14.
  • the larger high pressure chamber has an inside diameter of 203 mm (8 inches), a usable length of 1200 mm (4 feet) and is loadable up to about 550 bar (55 MPa, 7,975 psi).
  • tests for internal pressure resistance burst pressure test
  • tests for external pressure resistance ie pressurization of the internal pressure separator
  • tests for external pressure resistance ie exposure to the external pressure separator
  • the experimental set-up and implementation are in accordance with ISO 17824, First Edition, 2009-08-15 , Collapse pressure test and B (Burst pressure test) construction and method.
  • the tests carried out in this high pressure chamber are carried out with separators whose diameter corresponds to the technically relevant diameters.
  • the pressure transfer medium used is a viscous mixture of methyl cellulose, water and limestone powder of different particle sizes in accordance with ISO 17824 Annex A.4 (fluid loss control pill).
  • the task of the pressure transfer medium is to block the filter gaps and seal them so that a pressure difference can be built up.
  • separators are used, in which the outer diameter of the annular discs and the base tube is varied (see Table 4).
  • the separators are constructed with a steel L80Cr13 base tube and a ring stack of 80 annular sintered silicon carbide ceramic discs (SSiC; 3M TM silicon carbide type F, manufacturer: ESK Ceramics GmbH & Co. KG).
  • the effective length of the separators ie the height of the ring stack, is 500 mm.
  • the filter width is 250 ⁇ m.
  • the diameter of the base pipe is 59.6 mm (2 7/8 inches) in Examples Nos. 15 and 18, 88.9 mm (31 ⁇ 2 inches) in Example Nos. 16 and 139.7 mm (5 1 ⁇ 2 inches) in Examples No. 17 and 19.
  • Examples Nos. 15 to 17 are according to the invention, and examples Nos. 18 and 19 are reference examples.
  • the embodiment of the separation device in Examples Nos. 15 to 17 is carried out according to the Figures 3 a - 3 b.
  • the annular discs in Example No. 17 have 24 flat-faced spacers according to FIGS FIGS. 8 a - 8 g.
  • the embodiment of the annular discs in Examples Nos. 15 and 16 corresponds to that in FIGS FIGS. 8 However, instead of the 24 spacers shown therein, the annular discs have only 16 (Example No. 15) and 18 (Example No. 16) equally spaced spacers on top of the annular discs.
  • the separators of Examples Nos. 15 to 17 are according to Figures 3 a - 3 b with three spring steel bands for centering the ring stack (acc FIG.
  • a sealing bush at both ends of the ring stack in each case one end cap at both ends of the ring stack and with two compensating bushes made of PTFE between sealing bushes and end caps (according to FIGS Figures 12 a - 12 c).
  • the length of the PTFE compensation bushings is 16 mm.
  • annular disc separators having spherical segment spacers are shown in FIG FIG. 2 of the WO 2011/120539 A1 used. In these two examples, compression springs are used at both ends of the ring stack for clamping the ring stack.
  • test results show the significantly higher internal and external pressure resistance of the separation device according to the invention over the embodiment with spherical segment-shaped spacers on the annular discs and the tension of the ring stack with compression springs.

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Claims (23)

  1. Dispositif de séparation conçu pour la séparation de particules de matière par rapport à des liquides et/ou de gaz dans des forages de production, comprenant
    a) une pile d'anneaux (7) constituée par au moins trois disques en forme d'anneau durs et cassants (8), dans lequel le côté supérieur (9) des disques en forme d'anneau (8) comporte au moins trois écarteurs (10) régulièrement espacés sur la circonférence des disques, dont la surface de contact (11) est plane, si bien que les écarteurs (10) ont un contact plan avec le côté inférieur (12) d'un disque annulaire adjacent (8), et dans lequel les disques en forme d'anneau (8) sont empilés et fixés de telle manière qu'entre les différents disques (8) il y a respectivement une fente de séparation (14) conçue pour la séparation de particules de matière solide, et dans lequel la projection axiale des disques en forme d'anneau (8) est circulaire sur les circonférences intérieure et extérieure, et dans lequel le matériau dur et cassant des disques en forme d'anneau (8) est choisi parmi des matériaux céramiques oxydiques et non oxydiques, des céramiques mixtes constituées par ces matériaux, des matériaux céramiques avec l'adjonction de phases secondaires, des matériaux mixtes contenant des parts de matériaux durs céramiques ou métalliques et à phase métallique liante, des matériaux de métallurgie des poudres avec des phases de matières dures constituées in situ et des matériaux céramiques renforcés par des fibres longues et/ou courtes,
    b) un tube perforé (1) placé à l'intérieur de la pile d'anneaux (7) et sur lequel sont empilés les disques en forme d'anneau durs et cassants (8),
    c) au moins trois bandes (15) fixées de façon axialement parallèle et à une distance régulière sur la surface latérale (21) du tube perforé (1) placé à l'intérieur de la pile d'anneaux (7) sur lesquelles les disques en forme d'anneau (8) sont glissés, grâce auxquels ces disques en forme d'anneau (8) sont centrés sur le tube perforé (1), et
    d) un embout (5) sur l'extrémité supérieure et un embout (6) sur l'extrémité inférieure de la pile d'anneaux (7), où ces embouts (5, 6) sont fermement reliés au tube perforé (1).
  2. Dispositif de séparation conçu pour la séparation de particules de matière par rapport à des liquides et/ou de gaz dans des forages de production, comprenant
    a) une pile d'anneaux (32) constituée par au moins trois disques en forme d'anneau durs et cassants (28, 31) dans lequel le côté supérieur (29) et le côté inférieur (30) d'un disque annulaire sur deux (28) présentent sur la pile d'anneaux (32) au moins trois écarteurs (10) régulièrement espacés sur la circonférence des disques (28), et dans lequel les disques en forme d'anneau adjacents respectifs (31) ne comportent pas d'écarteurs, et dans lequel la surface de contact (11) des écarteurs (10) est plane, si bien que les écarteurs (10) ont un contact plan avec les disques en forme d'anneau adjacents (31), et dans lequel les disques en forme d'anneau (28, 31) sont empilés et fixés de telle manière qu'entre les différents disques (28, 31) il y a respectivement une fente de séparation (14) conçue pour la séparation de particules de matière solide, et dans lequel la projection axiale des disques en forme d'anneau (28, 31) est circulaire sur les circonférences intérieure et extérieure, et dans lequel le matériau dur et cassant des disques en forme d'anneau (28, 31) est choisi parmi des matériaux céramiques oxydiques et non oxydiques, des céramiques mixtes constituées par ces matériaux, des matériaux céramiques avec l'adjonction de phases secondaires, des matériaux mixtes contenant des parts de matériaux durs céramiques ou métalliques et à phase métallique liante, des matériaux de métallurgie des poudres avec des phases de matières dures constituées in situ et des matériaux céramiques renforcés par des fibres longues et/ou courtes,
    b) un tube perforé (1) placé à l'intérieur de la pile d'anneaux (32) et sur lequel sont empilés les disques en forme d'anneau durs et cassants (28, 31),
    c) au moins trois bandes fixées de façon axialement parallèle (15) et à distance uniforme sur la surface latérale (21) du tube perforé (1) placé à l'intérieur de la pile d'anneaux (32) sur laquelle les disques en forme d'anneau (28, 31) sont glissés, grâce auxquels les disques en forme d'anneau (28, 31) sont centrés sur le tube perforé (1), et
    d) un embout (5) sur l'extrémité supérieure et un embout (6) sur l'extrémité inférieure de la pile d'anneaux (32), de telle sorte que ces embouts (5, 6) sont solidement reliés au tube perforé (1).
  3. Dispositif de séparation selon la revendication 1, dans lequel le côté supérieur (9) des disques en forme d'anneau (8) est descendant vers l'intérieur ou l'extérieur dans les zones placées entre les écarteurs (10), de préférence descendant vers l'intérieur.
  4. Dispositif de séparation selon la revendication 2, dans lequel le côté supérieur (29) et le côté inférieur (30) d'un disque annulaire sur deux (28) dans la pile d'anneaux (32) sont descendants vers l'intérieur ou l'extérieur dans les zones placées entre les écarteurs (10), de préférence descendants vers l'intérieur.
  5. Dispositif de séparation selon la revendication 1 ou 3, dans lequel le côté inférieur (12) des disques en forme d'anneau (8) est configuré à angle droit par rapport à l'axe des disques.
  6. Dispositif de séparation selon la revendication 2 ou 4, dans lequel le côté supérieur et le côté inférieur des disques en forme d'anneau (31) qui ne comportent pas d'écarteurs sont configurés à angle droit par rapport à l'axe des disques.
  7. Dispositif de séparation selon l'une des revendications 1 à 6, dans lequel le dispositif de séparation résiste à des pressions intérieures atteignant jusqu'à 12 MPa (120 bar) dans le test de résistance à la pression intérieure selon ISO 17824 et des pressions extérieures atteignant jusqu'à 50 MPa (500 bar) dans le test de résistance à la pression extérieure selon ISO 17824.
  8. Dispositif de séparation selon l'une des revendications 1 à 7, dans lequel la surface de contact (11) des différents écarteurs (10) couvre 4 à 60 mm2, de préférence 10 à 35 mm2.
  9. Dispositif de séparation selon l'une des revendications 1 à 8, dans lequel le nombre des écarteurs (10) régulièrement espacés sur les disques en forme d'anneau (8, 28) est supérieur à 3, de préférence au nombre d'au moins 6, et mieux encore d'au moins 10 et mieux encore d'au moins 15.
  10. Dispositif de séparation selon l'une des revendications 1 à 9, dans lequel la distance entre les écarteurs (10) est de 8 à 50 mm, de préférence 10 à 30 mm et mieux encore, de 15 à 25 mm.
  11. Dispositif de séparation selon l'une des revendications 1 à 10, dans lequel le matériau dur et cassant est du carbure de silicium (SSiC) ou du carbure de bore fritté.
  12. Dispositif de séparation selon l'une des revendications 1 à 11, dans lequel le diamètre intérieur des disques en forme d'anneau (8, 28, 31) est plus grand d'au minimum 0,5 mm et d'au maximum 10 mm, de préférence d'au minimum 1,5 mm et d'au maximum 5 mm, que le diamètre extérieur du tube perforé (1).
  13. Dispositif de séparation selon l'une des revendications 1 à 12, dans lequel le dispositif de séparation comprend une cage de protection (4) assurant la protection contre les dommages mécaniques.
  14. Dispositif de séparation selon l'une des revendications 1 à 13, dans lequel le dispositif de séparation inclut une douille de joint (16) sur l'extrémité supérieure et une douille de joint (17) sur l'extrémité inférieure de la pile d'anneaux (7, 32).
  15. Dispositif de séparation selon l'une des revendications 1 à 14, dans lequel le dispositif de séparation à l'extrémité supérieure de la pile d'anneaux (7) et/ou sur l'extrémité inférieure de la pile d'anneaux (7, 32) inclut une douille de compensation (22, 23) en vue de compenser les différentes variations thermiques de longueur du tube perforé (1) et de la pile d'anneaux (7, 32).
  16. Dispositif de séparation selon la revendication 15, dans lequel le coefficient de dilatation thermique du matériau de la douille de compensation (22, 23) atteint au minimum 25 * 10-6 / K, de préférence au minimum 80 * 10-6 / K et mieux encore au minimum 100 * 10-6 / K sur une plage de température de 10 - 200 °C.
  17. Dispositif de séparation selon la revendication 15 ou 16, dans lequel la douille de compensation (22, 23) est réalisée en un matériau sur la base de polytétrafluoréthylène (PTFE).
  18. Dispositif de séparation selon l'une des revendications 1 à 17, dans lequel le dispositif de séparation à l'extrémité supérieure de la pile d'anneaux (7, 32) et/ou sur l'extrémité inférieure de la pile d'anneaux (7, 32) comprend un récipient (24, 25) tubulaire, à double paroi, rempli d'un liquide, dont les parois extérieures sont ondulées dans le sens axial, en vue de compenser les différentes variations thermiques de longueur du tube perforé (1) et de la pile d'anneaux (7, 32).
  19. Dispositif de séparation selon l'une des revendications 1 à 18, dans lequel le tube perforé (1) est fabriqué en un matériau dont le coefficient de dilatation thermique sur une plage de température de 10 °C à 200 °C diverge d'un maximum de 10 %, de préférence d'un maximum de 5 %, du coefficient de dilatation thermique du matériau de la pile d'anneaux (7, 32) sur une plage de température de 10 °C à 200 °C.
  20. Dispositif de séparation selon l'une des revendications 1 à 19, dans lequel les disques en forme d'anneau (8, 28, 31) sont fabriqués en céramique d'oxyde de zirconium, et dans lequel le coefficient de dilatation thermique de la céramique d'oxyde de zirconium sur une plage de température de 10 °C à 200 °C diverge d'un maximum de 10 %, de préférence d'un maximum de 5 %, du coefficient de dilatation thermique du matériau du tube perforé sur une plage de température de 10 °C à 200 °C.
  21. Dispositif de séparation selon l'une des revendications 1 à 20, dans lequel la tension préalable exercée sur la pile d'anneaux (7, 32) dans le sens axial sur une plage de température de 10 °C à 200 °C atteint au maximum 10 MPa, de préférence au maximum 5 MPa, et mieux encore, au maximum 2 MPa, par rapport à la surface de projection axiale des disques en forme d'anneau.
  22. Dispositif de séparation selon l'une des revendications 1 à 21, dans lequel le décalage des disques en forme d'anneau (8, 28, 31) dans la pile d'anneaux (7, 32) provoqué par les différences de pression du liquide pendant le fonctionnement du dispositif de séparation sur une plage de température de 10 °C à 200 °C n'est pas supérieur à 1,5 pour mille dans le sens axial, par rapport à la longueur de la pile d'anneaux.
  23. Utilisation d'un dispositif de séparation selon au moins l'une des revendications qui précèdent, conçu pour la séparation de particules de matière par rapport à des liquides et/ou des gaz, dans un procédé d'acheminement de liquides et/ou de gaz dans des forages de production.
EP14179128.5A 2014-07-30 2014-07-30 Dispositif de séparation destiné à séparer des particules de matière solide d'écoulements gazeux et liquides pour des pressions différentielles élevées Active EP2980348B1 (fr)

Priority Applications (11)

Application Number Priority Date Filing Date Title
ES14179128.5T ES2640477T3 (es) 2014-07-30 2014-07-30 Separador para separar partículas sólidas de flujos de líquidos y gases para altas presiones diferenciales
EP14179128.5A EP2980348B1 (fr) 2014-07-30 2014-07-30 Dispositif de séparation destiné à séparer des particules de matière solide d'écoulements gazeux et liquides pour des pressions différentielles élevées
DK14179128.5T DK2980348T3 (en) 2014-07-30 2014-07-30 SEPARATOR FOR SEPARATING SOLID PARTICLES FROM HIGH-DIFFERENCE LIQUID AND GAS FLOWS
MX2017001260A MX2017001260A (es) 2014-07-30 2015-07-27 Dispositivo de separacion para eliminar particulas solidas de flujos de liquido y gas para presiones diferenciales altas.
CN201580041600.5A CN106574494B (zh) 2014-07-30 2015-07-27 用于从液体和气体流移除固体颗粒以用于高压差的分离装置
PCT/US2015/042288 WO2016018821A1 (fr) 2014-07-30 2015-07-27 Dispositif de séparation permettant d'éliminer des particules solides dans des écoulements de liquide et de gaz pour des pressions différentielles élevées
AU2015296866A AU2015296866B2 (en) 2014-07-30 2015-07-27 Separating device for removing solid particles from liquid and gas flows for high differential pressures
US15/329,983 US10415351B2 (en) 2014-07-30 2015-07-27 Separating device for removing solid particles from liquid and gas flows for high differential pressures
RU2017102753A RU2645393C1 (ru) 2014-07-30 2015-07-27 Сепарирующее устройство для удаления твердых частиц из потоков жидкости и газа для больших перепадов давления
CA2956483A CA2956483A1 (fr) 2014-07-30 2015-07-27 Dispositif de separation permettant d'eliminer des particules solides dans des ecoulements de liquide et de gaz pour des pressions differentielles elevees
BR112017001857A BR112017001857A2 (pt) 2014-07-30 2015-07-27 dispositivo de separação para remoção de partículas sólidas de fluxos de líquido e gás sob altas pressões diferenciais

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CA (1) CA2956483A1 (fr)
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ES (1) ES2640477T3 (fr)
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EP3604734B1 (fr) * 2018-08-01 2021-10-20 3M Innovative Properties Company Dispositif de séparation et utilisation d'un dispositif de séparation
CN113167111A (zh) * 2018-12-10 2021-07-23 3M创新有限公司 分离装置和分离装置的用途
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EP3670828A1 (fr) * 2018-12-18 2020-06-24 3M Innovative Properties Company Dispositif de séparation et utilisation d'un dispositif de séparation
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Also Published As

Publication number Publication date
BR112017001857A2 (pt) 2017-11-21
RU2645393C1 (ru) 2018-02-21
AU2015296866B2 (en) 2018-03-29
AU2015296866A1 (en) 2017-02-16
US10415351B2 (en) 2019-09-17
MX2017001260A (es) 2017-05-01
US20170254185A1 (en) 2017-09-07
WO2016018821A1 (fr) 2016-02-04
CN106574494A (zh) 2017-04-19
CN106574494B (zh) 2019-10-11
CA2956483A1 (fr) 2016-02-04
ES2640477T3 (es) 2017-11-03
DK2980348T3 (en) 2017-10-02
EP2980348A1 (fr) 2016-02-03

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