EP2553216B1 - Dispositif de séparation résistant à l'usure pour la séparation de particules de sable et de particules de roche - Google Patents

Dispositif de séparation résistant à l'usure pour la séparation de particules de sable et de particules de roche Download PDF

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Publication number
EP2553216B1
EP2553216B1 EP10715683.8A EP10715683A EP2553216B1 EP 2553216 B1 EP2553216 B1 EP 2553216B1 EP 10715683 A EP10715683 A EP 10715683A EP 2553216 B1 EP2553216 B1 EP 2553216B1
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EP
European Patent Office
Prior art keywords
separating device
clamping
discs
materials
annular
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.)
Active
Application number
EP10715683.8A
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German (de)
English (en)
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EP2553216A1 (fr
Inventor
Stefanie Wildhack
Armin Kayser
Samuel Joly
Siegfried MÜSSIG
Klaus Wahrmann
Fabian PÖHLING
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ESK Ceramics GmbH and Co KG
Total E&P Danmark AS
Original Assignee
ESK Ceramics GmbH and Co KG
Maersk Olie og Gas AS
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Publication of EP2553216A1 publication Critical patent/EP2553216A1/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
    • E21B43/082—Screens comprising porous materials, e.g. prepacked screens
    • 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
    • E21B43/088—Wire screens

Definitions

  • the invention relates to a novel separation device with improved erosion and abrasion resistance, which is an integral part of a production equipment for use in the extraction of oil, water and gas mixtures or their individual components from deep wells, with their help solids such as sand and rock particles can be separated from the liquids and gases to be delivered.
  • the separator is used in particular to prevent the erosive and abrasive removal of the conveyor equipment by sand and rock particles. At the same time the separator is corrosion resistant to treatment liquids.
  • a major disadvantage of these designs with metallic wire mesh, wire mesh or wire windings is their low resistance to wear. Due to the abrasive or erosive effect of the sand and rock particles flowing in with high flow velocity, the filters are destroyed and the delivery pipes are damaged. At the same time the productivity of the promotion decreases, since now the sand is no longer effectively filtered out but is transported on with the pumped medium. Another problem is the corrosive wear on the filters and delivery pipes caused by the use of treatment liquids. This corrosive wear in turn increases the abrasive wear. Treatment liquids, such as acids, alkalis, water or superheated steam, are used to clean the separator and to stimulate the wellbore.
  • Treatment liquids such as acids, alkalis, water or superheated steam
  • Another problem is that the abrasion resistance of porous ceramic materials is significantly lower than that of dense ceramic materials.
  • a disadvantage of this solution is that the improved wear protection is accompanied by an energy dissipation of the flowing medium; the outer sleeve does not act as a filter but as a flow resistance that degrades the flow rate. It is not disclosed how the cuff is mounted on the conveyor tube.
  • a cylindrical sieve filter which includes a plurality of stacked annular filter segments.
  • the ring stack is held together by a plurality of threaded rods with threaded nuts or double nuts made of stainless steel at the top and bottom.
  • the separation of the particles takes place at the variable annular gap, which is formed between opposite filter segments.
  • the rings are made of plastic, preferably of glass-reinforced polypropylene (column 4, Z. 50-54).
  • the threaded rods are guided through openings provided in the rings (column 4, lines 31-33). This solution can not be realized from ceramics.
  • the cross-sectional transitions are edged;
  • the filter segments have a typical plastic design.
  • the invention has for its object, overcoming the disadvantages of the prior art, to provide a separator for the separation of sand and rock particles in the promotion of liquids or gases from rock drilling available, the better wear and abrasion resistance and a lower tendency to fracture as the known in the prior art separation devices, and which is also resistant to corrosion treatment fluids, and can withstand the loads occurring during the promotion, has a longer life and with their help higher flow rates can be achieved.
  • the separator should moreover be suitable as an integral part of a conveying equipment for conveying liquids or gases from deep wells.
  • the invention also relates to the use of the separation device according to the invention for the separation of sand and rock particles in a process for the promotion of liquids or gases from rock or deep wells.
  • the annular disks of the separating device according to the invention are stacked and braced so that they are axially fixed and forms between the individual disks each have a defined separation gap for the separation of sand and rock particles.
  • the rings are movable relative to each other to a certain extent, whereby a stress build-up in the ring stack is effectively reduced by external loads such as bending.
  • the ring stack is fixed on the tensioning device only in itself, the sand filter module requires no additional mechanical support. For example, it is not fastened to an inner conveyor tube which carries the dead weight of ring stack and tensioning device and optionally further coupling elements, intermediate modules and / or the filter module tip.
  • the separation device further comprises one or more protective sheaths for protecting the intermediate modules and the coupling elements.
  • the separation device according to the invention constructed from brittle-hard ring elements is more resistant to abrasion and corrosion than conventional sand-combing devices. It therefore has a longer service life than the sand filters of the prior art.
  • the separation device according to the invention must therefore, in contrast to the sand filters of State of the art can not be replaced at regular intervals, so that the intervals until an existing hole has to be overhauled (workover), significantly longer.
  • the present invention allows the favorable ceramic material properties of the ceramic materials, in particular their abrasion resistance and their high deformation resistance, to be used for the highly abrasive sand filter by the ceramic design solution.
  • the unfavorable for this class of materials loads, in particular point, bending, tensile and impact loads are avoided constructively by the inventive solution.
  • annular discs Due to the high resistance of the brittle-hard discs against deformation, the annular discs must in contrast to the prior art (such as in the US 5,515,915 ) are not supported by spacer and support rods on an inner tube to increase their stability in the stack and each other. They can be free-standing.
  • annular discs Once the annular discs are axially braced, they form a very stable separation gap, which has a small tolerance width, which is due only to the manufacturing tolerance of the rings and not by material deformability.
  • the separation gap widths comply with the standard API guidelines (American Petroleum Institute) and can even surpass these standards.
  • the high resistance to mechanical deformation caused, for example, by incident sand layers prevents the separation gaps from changing.
  • sand filters of wire mesh and wire windings In contrast to the prior art sand filters of wire mesh and wire windings, clogging of the separation gaps is inhibited.
  • multi-ply filter fabrics are common and necessary for protecting the fine filter.
  • the multi-layer fabric arrangement increases the flow resistance.
  • Multi-ply fabrics also tend to become clogged by the deposition of sands in the cavities, and thus to further increased flow resistance.
  • the inventive ceramic sand filter modules can be made in one layer due to the good abrasion resistance and the high resistance to deformation of the brittle ring stack and be charged directly with the flow.
  • An additionally introduced filter gravel pack between filter and inner tube as a secondary filter is not necessary in the ceramic sand filter modules according to the invention. Instead, the sand and rock particles to be separated can build up on the outer peripheral surface of the stable, brittle-hard discs as a secondary filter cake. Its stability is favored by the separator according to the invention, which leads to an increase in the well integrity.
  • the separation of the particles is ensured in direct inflow and through flow, without the flow being negatively influenced by deflection or energy dissipation.
  • the pressure loss of the separator according to the invention is negligible and the separator according to the invention is flowed through laminar.
  • the separation device according to the invention requires no mechanical support as the plastic filter segments in the US 5,249,626 or the metallic wire mesh of the US 5,624,560 .
  • the ring stack according to the invention is fixed on the clamping device only in itself and is not supported or supported by an inner conveyor pipe. Since the inner delivery pipe is eliminated, thus also the existing inside the free conveying cross section and thus the delivery rate is increased.
  • the resilient mounting of the ring stack allows bends to be accommodated and different thermal expansions of the different materials to be compensated.
  • the rings are stacked and braced so that they are movable in the radial and tangential direction to a certain extent against each other, whereby a stress build-up in the ring stack is effectively reduced by external stresses such as bending.
  • the sand filter modules can be attached to existing delivery systems using conventional connection technology. This applies both to the attachment at the end of the conveyor linkage as well as for a subsequent insertion of the filter modules and hanging on a landing nipple.
  • the individual sand filter modules can be connected via the coupling elements and intermediate modules to filter systems of any length.
  • the separating device according to the invention can be used under any wellbore deflection, both in the horizontal and in the vertical wellbore and also under any other borehole inclination, for example at a borehole inclination of 60 °. This is an advantage over the conventionally used metallic wire mesh.
  • the separating device according to the invention preferably comprises filter module tips with increased abrasion protection.
  • FIG. 1 shows the overall view of a separation device according to the invention, which is modularly composed of at least one ceramic filter module 1 (hereinafter also referred to as “sand filter module”).
  • the separation device can be arbitrarily extended by the modular structure.
  • the separator comprises at the lower end of the lowermost sand filter module and thus at the end of the drill string a filter module tip 2.
  • the ceramic sand filter modules take over the sand separation or sand control.
  • the sand filter modules can also be connected via intermediate modules 3 with other sand filter modules.
  • the intermediate modules can perform various tasks, such as ensuring sufficient bending when introducing the separator into the well, the centering of the separator in the well casing or the attachment / anchoring of the separator to the production tubing or well casing. It is also possible to use active elements as intermediate modules, by means of which backwashing or free-flowing of added filter elements is realized.
  • the separation device according to the invention can be installed both in the re-equipment of sand-carrying holes as well as in the overhaul of the hole (Workover) in the conveyor system, further it can also be introduced in an existing hole through the interior of the production tubing and anchored to the landing nipples of the well casing , Depending on the application variant, the intermediate modules and the geometric data of the ceramic sand filter modules differ, but the design principles can be retained.
  • the annular discs 7 used in the ceramic sand filter module are in the Figures 2a - 2d and 3a - 3d for two preferred embodiments of the sand filter module shown.
  • Figure block 2 shows the design of the annular discs for a first embodiment, at the internal clamping rods 14 (s. FIG. 6 ) are used for clamping the ring stack.
  • the ring stack is placed on an inner, perforated tube 15 (see FIG. FIG. 7 ) and braced, the rings used for this shows Figure block 3.
  • the annular discs are made of a brittle-hard material, preferably made of a ceramic material that is resistant to abrasion and erosion against the sand and rock particles and corrosion resistant to the fluids and the media used for cleaning such as acids.
  • the separation of the sand and rock particles takes place at a radial, preferably tapered gap 9 (s. Figures 5 and 6 ), which forms between two superimposed, strained ring elements.
  • the ring elements are designed ceramics appropriate or brittle hard materials, ie cross-sectional transitions are performed without notches and the formation of bending stresses is constructively avoided or compensated.
  • the height (thickness) of the annular discs depends on the required flow rate.
  • the annular discs 7 have on their upper side 16 at least three evenly distributed over the circumference of the discs elevations 8 with a defined height, with the help of the height of the separating gap (gap width) is set.
  • the elevations are not separately applied or subsequently welded spacers. They are formed directly during manufacture during the shaping of the annular discs.
  • the elevations are preferably in the form of spherical sections in order to achieve a point contact between opposing annular discs and to avoid surface contacts.
  • the annular discs preferably have on their outer peripheral surface a recess / marking groove 17, by means of which the annular discs are more easily positioned one above the other during installation and thus fail-safe mounting is allowed.
  • the marking groove is preferably rounded.
  • the upper surface 16 of the annular discs may be made at right angles to the disc axis or sloping inwardly or outwardly sloping with a plane or curved surface.
  • the underside 18 of the annular discs may be designed to slope outwards or inwards, preferably inwardly sloping, more preferably it is concave.
  • An inwardly sloping design is advantageous in terms of a reduced tendency to clog the separator.
  • the concave shape is to understand the ring bottom as a whole, see Figures 2d and 3d , Here, the ring bottom is designed with a radius R.
  • the annular discs in the ring stack are movable relative to each other in the radial and tangential direction, whereby a stress build-up in the ring stack is effectively reduced by external stresses such as bending.
  • the cross-sectional shape of the annular discs is preferably non-rectangular and not trapezoidal due to the concavely curved surfaces. It also has no sharp edges and cross-sectional transitions.
  • the outer contours 19 of the annular discs are chamfered, as in FIG Figures 2d and 3d illustrated.
  • the edges may also be rounded. This represents an even better protection of the edges from the edge load which is critical for brittle-hard materials.
  • the peripheral surfaces (cladding surfaces) of the annular discs are preferably cylindrical (even). But it is also possible to form the peripheral surfaces outwardly convex, for example, in order to achieve a better flow.
  • the radial wall thickness of the annular discs is preferably at least 2 mm, more preferably at least 5 mm.
  • the height or thickness of the discs is preferably 1 to 20 mm, more preferably 1 to 10 mm.
  • the outer diameter of the annular discs is smaller than the inner diameter of the borehole or as the inner diameter of the Bohrlochfutterrohres. It is usually 50-200 mm. Also possible are smaller diameters than 50 mm and larger than 200 mm.
  • the inner diameter of the annular discs is preferably less than 90%, more preferably less than 85% of the outer diameter of the annular discs.
  • the contour of the inner diameter of the annular discs can also be approximated by a polygon, for example a hexagon.
  • the inner diameter of the annular discs must additionally be greater than the diameter of the inner, perforated tube.
  • the annular discs must not rest on the inner tube. This ensures that the deflection occurring during the insertion into the borehole can be absorbed via the construction of the ring stack and a breakage of the ceramic elements is avoided.
  • the annular discs preferably have at least three recesses / grooves 20 (s. FIG. 2 a) , which serve to accommodate the tension rods. If the contour of the inner diameter of the annular discs is formed as a polygon, the recesses can be omitted since the tension rods can be guided in the corners.
  • These recesses 20 are offset from the distributed on the top elevations 8 are mounted in a preferred embodiment, six grooves 20 are introduced on the peripheral surface.
  • the three elevations 8 on the top 16 are arranged so that they are located in each second space between two grooves 20.
  • the recesses 20 are preferably formed rounded (s. FIG. 2 a) ,
  • the discs allow a very simple assembly by means of the grooves on the inner diameter of the annular discs. Since the wall thickness in the region of the grooves is reduced, however, it is possible in this variant, especially with small available Bohrlochfutterrohr- and delivery pipe diameters, to reduce the ring stability and thus to restrictions in use.
  • the panes have an almost uniform wall thickness over the entire circumference and can thus be used under extreme geometric requirements.
  • the underside 18 of the rings additionally at least three recesses 21, (s. FIG. 3 c) in which the elevations 8 of the opposite top of the next ring segment can be positioned.
  • the number and the distance of the recesses depend on the number and distance of the elevations on the ring top.
  • the recesses are used to prevent rotation of the rings and support the self-centering of the rings in the stack.
  • these recesses are not necessary, since here the rotation takes place sufficiently over the tension rods. It can still be made recesses on the underside of the ring. Since these are associated with overhead in the production, they are preferably eliminated.
  • the depressions are preferably surfaces displaced parallel to the radius R (see FIG. FIG. 3 a) , In this way, point contact with the surveys is ensured, and the three-point support compensates for possible deviations in shape and dimensions.
  • the depressions can also be formed in the form of spherical or cylindrical sections. Also a rounded trapezoidal shape or a wavy structure is possible.
  • the gap width 9 (s. FIG. 4 and 5 ) is selected depending on the sand fraction to be separated. At the outer diameter, the gap width is the smallest, in order to avoid clogging of the annular gap.
  • the gap width is set by the height of the elevations on the top of the ring, the depth of the recesses on the underside of the ring (if present) and the shape of the underside of the ring, ie the radius of the concave surface.
  • the selected gap geometry ensures that the flow processes in the gap are laminar and that the pressure loss between outer and inner diameter is low.
  • the separation device can be backwashed by liquid treatment media, possibly introduced particles in the separation gap can be rinsed free.
  • the brittle-hard material of the annular discs is preferably 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 hard materials and metallic binder phase, precipitation hardened cast materials, powder metallurgy materials with in-situ formed hard material phases and long and / or short fiber reinforced ceramic materials.
  • oxidic ceramic materials are 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 ceramic materials is C-SiC.
  • the above-mentioned materials are characterized by being harder than the typically occurring rock particles, ie the HV or HRC hardness values of these materials are above the corresponding values of the surrounding rock.
  • suitable materials 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”.
  • all these materials have a very high deformation resistance, which is reflected in their modulus of elasticity.
  • the high rigidity has a positive effect on the abrasion behavior of the materials. A peeling of material and a plastic deformation as in metals is not possible here.
  • the structure of the sand filter module is also positively influenced by the high resistance to deformation.
  • the annular discs made of these materials need not be supported by webs on an inner tube in order to increase their stability in the stack and each other. They can be free-standing. As soon as they are braced axially, they form a very stable separating gap, which has a small tolerance width, which is only due to the manufacturing tolerance of the rings and not due to material deformability. Even with sudden loads they do not deform, the set separation gap width is retained.
  • suitable materials have elastic moduli 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 corrosion 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, e.g. HCl, lyes, e.g. NaOH, or water vapor.
  • SSiC materials with fine-grained microstructure are particularly suitable, for example, SSiC materials with fine-grained microstructure (mean particle size ⁇ 5 microns), as they are selling KG, for example, under the name EKasic ® F and EKasic ® F plus from ESK Ceramics GmbH & Co..
  • coarse-grained SSiC materials for example with a bimodal microstructure, with preferably 50 to 90% by volume of the particle size distribution consisting of prismatic, platelet-shaped SiC crystallites having a length of 100 to 1500 ⁇ m and 10 to 50% by volume. of prismatic, platelet-shaped SiC crystallites of a length of 5 to less than 100 microns (EKasic ® C from ESK Ceramics GmbH & Co. KG).
  • the production of the annular disks is possible by means of powder metallurgy or ceramic processes in an automated mass production.
  • the ring-shaped disks can be produced in the so-called net-shape process, in which the annular disks (including elevations) are pressed out of near-net shape powders.
  • a complex mechanical processing of the annular discs is not required.
  • the shape and dimensional deviations in the individual annular disks, which are sometimes unavoidable in a sintering process, can be tolerated in a design according to the invention of the separating device.
  • the ring discs made of brittle-hard materials are mounted together with the coupling elements as a ring stack of any height.
  • the ring stack height and thus the sand filter module length is based on the hole diameter requirements, the resulting loads, the required bending and the load capacity of the metallic clamping structure.
  • a preferred height of the ring stack or the filter length is 1000 mm.
  • FIGS. 4 a - 4 c and 5a - 5 c show inventive ring stack 6 with the coupling elements 10 and 11.
  • Die FIGS. 4 a - 4 c show the embodiment with the tension rods 14 (s. FIG. 6 ).
  • the Figures 5 a - 5 c show the embodiment with the inner clamping tube 15 (s. FIG. 7 ).
  • the FIGS. 4a and 5a are plan views of the upper coupling element 10.
  • the Figures 4b, 4c . 5b and 5c are respectively cross-sectional views along each of the line BB in the FIGS. 4a and 5a or along each of the line AA in the FIGS. 4 a and 5 a.
  • the coupling elements in each case form the end-side, lateral terminations of the ring stack, via which the ring stack is coupled to the tensioning device. They are designed so that the clamping forces are transmitted evenly to the ring stack.
  • the coupling elements are preferably made of the same material as the rings. Alternatively, however, corrosion-resistant steels and plastics such as fluoroelastomers or PEEK (polyetherketone) can be used.
  • the upper surface of the upper coupling element 10, which is directed to the clamping device, preferably has a flat / flat surface.
  • the surface directed toward the ring stack, that is to say the underside of the coupling element 10, is preferably designed with a radius, ie, like the ring elements, it is concave.
  • the outer circumferential surface preferably has a circumferential groove 22 (FIG. FIGS. 4 and 5 ) for receiving a sealing ring (O-ring) 23 (in FIGS. 8 a and 9 a) and preferably a recess / marking groove 24 (FIG. FIGS. 4 and 5 ) for positioning the coupling elements in relation to the ring elements.
  • the marking groove 24 is preferably rounded.
  • the lower surface of the lower coupling member 11, which faces the tensioning device, preferably has a flat surface.
  • the surface directed toward the ring stack, that is to say the top side of the coupling element 11, has at least three elevations distributed uniformly over the circumference of the disks.
  • the outer peripheral surface is preferably a circumferential groove 22 for receiving a sealing ring (O-ring) 23 (in FIGS. 8 a and 9 a) and preferably a recess / marking groove 24 for positioning the coupling elements in relation to the ring elements.
  • the marking groove 24 is preferably rounded.
  • the inner diameter of the coupling elements corresponds to that of the ring elements.
  • the outer diameter of the coupling elements is preferably equal to or greater than that of the annular discs (s. FIGS. 4 or 5). Due to the geometric conditions, however, it may be necessary constructively that the outer diameter fails slightly smaller than the outer diameter of the annular discs. However, this is only possible if the smallest wall thickness does not fall below 2 mm and the component and handling stability is not endangered.
  • At least three recesses / grooves 25 are preferably additionally provided on the inner peripheral surface of the coupling elements 10 and 11, which serve to receive the tension rods. These recesses are offset from the distributed on the top of the annular discs surveys attached.
  • six grooves 25 are formed on the inner circumferential surface. The three elevations on the top are arranged so that they are located in each second space between two grooves.
  • the recesses 25 are preferably formed rounded (s. FIG. 4 a) ,
  • the tolerances of the two coupling elements 10, 11 are selected to be narrower than those of the annular discs in order to optimally couple the brittle-hard components to the metallic components of the clamping device; In contrast to the as-sintered ring disks, the coupling elements must be machined.
  • the upper surface of the upper coupling element 10 and / or the lower surface of the lower coupling element 11 is not flat / flat but designed as a spring seat. In this way, the springs are directly absorbed and additionally protected against the fluid.
  • the annular discs are mounted together with the coupling elements as a ring stack of any height and fixed by means of the clamping device in itself.
  • the task of the tensioning device is to brace the axially stacked ring elements in itself and set the defined separation gap between the individual discs set.
  • the width of the separating gap preferably has a value in the range of 0.05-1 mm, more preferably 0.05-0.5 mm.
  • the ring stack is fixed in the inventive sand filter module on the tensioning device only in itself, the sand filter module requires no additional mechanical support. For example, it is not fastened to an inner conveyor tube which carries the dead weight of the ring stack and the tensioning device and optionally further coupling elements, intermediate modules and / or the filter module tip. For this reason, the tensioning device must be able to absorb the tensile loads resulting from its own weight.
  • the clamping device preferably consists of an upper and lower clamping set and one or more clamping elements which connect the clamping sets and extend along the inner circumference of the ring stack.
  • the clamping element can be used, for example, as a clamping tube 15 (FIG. FIG. 7 ) or by at least three evenly distributed tension rods 14 ( FIG. 6 ).
  • the clamping set consists of clamping bush 26, compression springs 27 (both in FIG. 6 and 7 ) and clamping nuts 28 (in the embodiment with the tension rods, FIG. 6 ) and clamping ring 29 (in the embodiment with the tension tube, FIG. 7 ).
  • the clamping device allows a controlled and uniform force on the coupling elements and thus on the ring stack. This is achieved to a large extent by the at least three evenly distributed compression springs 27. In a preferred embodiment, there are six evenly distributed compression springs 27.
  • the compression springs are preferably selected from corrosion-resistant steel, coated steel or corrosion-resistant elastomer such as rubber or Viton.
  • the clamping elements are preferably made of steel, more preferably made of corrosion-resistant steel. Since the clamping elements in the inner space of the ring stack are made of brittle-hard material, they are protected by it from abrasion and thus ensures the tension within the sand filter module over its entire life.
  • the clamping element is designed as a clamping tube 15 (FIG. FIGS. 7 and 9 ), which must have through flow openings for the promotion of oil, water and gas mixtures or their individual components from deep wells. It may be a perforated or slotted tube or a cylindrical perforated plate. The shape, arrangement and number of flow openings is determined on the one hand by the required flow rate and on the other by the desired tensile and torsional strength of the clamping tube. In the preferred embodiment in FIG. 9a the flow openings are formed as rounded slots 41. They are introduced into the clamping tube only in the area of the annular discs, from the coupling segments, the circumferential surface consists of solid material. On the upper and lower peripheral surface of the clamping tube 15 is preferably in each case an external thread 30 for attachment to the clamping ring.
  • a coarse-mesh sieve or a rigid wire mesh can be constructed and used as a tube.
  • the outer diameter of the clamping tube 15 is smaller than the inner diameter of the annular discs, so that a gap between clamping tube and ring stack is present.
  • the ring-shaped discs must not rest on the tensioning tube, so that external loads such as bending are not transferred by load transfer from the metallic tensioning tube to the rings.
  • spacers 31 made of an elastic, compressible polymer material between clamping tube and ring stack. This may be a wound polymer tape, polymer rings or polymer strips.
  • at least 3 are each offset by 120 ° from each other, the entire length of the ring stack and the coupling elements covering the polymer strips used, whereby the washers are additionally centered on the clamping tube.
  • a plurality of clamping elements in the form of tension rods 14 (FIG. FIGS. 6 and 8th ), evenly distributed over the inner circumference of the ring stack.
  • the tension rods can be received in the recesses / grooves 20 of the annular discs and correspond in number to the number of recesses / grooves 20.
  • the number of tension rods is selected depending on the required tension on the ring stack and the capacity for resulting from its own weight tensile loads of the modules.
  • the tension rods 14 may be designed with a round or ellipsoidal cross-sectional area.
  • To increase the material cross-section and thus the tensile and torsional strength of the tension rods are preferably used as profile bars 32 (FIG. Figures 8b and 8c ).
  • the cross-sectional area of the profiled bars may, for example, correspond to that of a circle segment or, as in the preferred embodiment, in FIGS. 8b or c a combination of ring and circle segments.
  • the tension rods can be provided with a powder coating to avoid direct contact of the steel material of the rods on the ceramic ring elements.
  • the profile cross section does not extend over the entire length of the clamping rods, but goes in the region of the clamping bushes in a round cross-sectional area 33 (FIGS. FIG. 8 a) above. Strictly speaking, the circular segment of the profile is extended in a round cross-sectional area.
  • a thread 34 FIG. 8 a
  • the clamping bush serves as a compression spring seat and has inner guides 35 (FIG. FIGS. 8 a, 8 c, 9 a) for receiving the compression springs, on the other hand it allows the tension on the clamping element / the clamping elements.
  • the clamping device is sealed to the outside, ie between clamping tube and coupling element by means of O-rings (23 in FIG. 9 a) ,
  • the clamping bush is preferably made of steel, more preferably made of corrosion-resistant steel.
  • clamping bushes are designed differently for the two preferred embodiments of the clamping elements.
  • the clamping bush is cylindrical ( FIG. 9 a) , Passing the outer peripheral surface of the outer cage is guided past the inner circumferential surface passes over the clamping tube.
  • On the surface facing the clamping ring is preferably a circumferential groove for receiving a sealing ring (O-ring, 36, FIG. 9 a) ,
  • the clamping bush is cylindrical on the inner circumferential surface, outside three areas can be distinguished: an outer guide 37 (FIG. FIG. 8 a) for receiving the outer cage, a recess 38 ( FIG. 8 a) for receiving an O-ring and a thread 39 for attachment to the coupling element.
  • an outer guide 37 FIG. FIG. 8 a
  • a recess 38 FIG. 8 a
  • a thread 39 for attachment to the coupling element.
  • through-holes 40 FIG. 8 c
  • the holes are on the to the clamping nuts aligned side designed as round holes, on the aligned to the coupling elements side they have a profile that can accommodate the profile of the tension rods.
  • clamping tube for clamping is preferably a clamping ring (29 in FIG. 9 a) used.
  • This is cylindrical on the inner circumferential surface and has a recess with internal thread 42 for screwing to the clamping tube to the side of the ring stack. Outside, three areas can be distinguished: an outer guide 43 for receiving the outer cage, a recess 44 for receiving an O-ring and a thread 45 for attachment to the coupling element.
  • the clamping of the ring stack is parallel to the assembly.
  • fixation of the tie rods or of the tensioning tube is preferably done via clamping nuts or a clamping ring, as applied as a defined torque and length tolerances can be compensated.
  • Alternative types of attachment to thread and locknut represent the combinations of groove and circlip and counterbore and grub screw. An attachment by welding, jamming or shrinking is possible.
  • the ring stack is braced more flexibly with the aid of the somewhat flexible tie rods in comparison to the embodiment with clamping tube.
  • tensile and torsional strength are higher in the embodiment with tension tube, the profile cross section of the tension rods ensures sufficient tensile strength to support the dead load.
  • the tie rods have sufficient strength to prevent large-scale twisting of the construction.
  • smaller deformations are possible and allow the rings in the ring stack in the radial and tangential direction in to move to a certain degree.
  • stress build-up in the ring stack can be more effectively reduced by bending than in the tension tube embodiment.
  • the sand filter module according to the invention is preferably protected against damage during installation such as impact load or friction on the well casing and when starting the promotion by rapidly flowing rock particles by a freely permeable outer cage 5 ( FIG. 1 ).
  • This can for example be designed as a coarse mesh screen and preferably as a perforated plate.
  • the material used is preferably steel, more preferably stainless steel.
  • the use of fiber-reinforced polymer materials is conceivable, since here the load-bearing capacity and the resistance to torsional and bending moments can be adjusted according to requirements.
  • the outer cage is loosely clamped in the outer diameter of the clamping device, but can also be firmly connected to the stiffening of the separator against bending and torsional and tensile and compressive stresses with the jig. This fixation is possible for example by gluing, screwing, pinning or shrinking, preferably the outer cage is welded to the clamping device after assembly.
  • Coupling elements for connecting the sand filter modules with other components of the conveying equipment
  • the coupling elements 12, 13 are used to connect the strained ring stack / sand filter module with other components of the conveying equipment such as the filter module tip 2 and intermediate modules.
  • the individual sand filter modules can be connected via the coupling elements and intermediate modules to filter systems of any length.
  • the coupling elements are preferably made of steel, more preferably made of corrosion-resistant steel.
  • the coupling element has an identical with the clamping device outer diameter and are cylindrical outside.
  • they Towards the intermediate module, they preferably show an outer conical wedge surface 47 (FIG. FIGS. 6 and 7 ).
  • the inner peripheral surface can be divided into three areas: In the middle region, the coupling element is tubular and has a consistently thick wall thickness. To the clamping device towards the pipe is tapered and reduces the wall thickness. In this area there is a thread 48 ( FIGS. 6 and 7 ) for attachment to the tensioning device. At the outer end is a further recess 49 ( FIG. 7 ), which receives a sealing ring (O-ring) 50.
  • the inner circumferential surface has an internal thread 51 (FIG. FIGS. 6 and 7 ). However, it is also conceivable that the thread is incorporated as an external thread in the outer peripheral surface.
  • coupling elements which connect to a filter module tip 2 are generally designed to be shorter than those which receive intermediate modules.
  • an internal cone 52 FIG. FIGS. 6 . 7 and 10
  • at least one circumferential groove 53, 54 FIG. FIGS. 6 . 7 and 10
  • a sealing ring 55 FIGS. 6 . 7 and 10
  • a snap ring 56 FIGS. 6 . 7 and 10
  • the length of the coupling elements; take the intermediate modules, is not critical and preferably rather to choose longer, since the coupling elements and intermediate modules must contribute depending on the chosen embodiment and thus rigidity of the tensioning device in addition to receiving external loads such as bending and resulting from its own weight tensile loads.
  • the outer, conical wedge surface of the coupling elements and the intermediate modules are preferably provided by one or more protective sheaths 4 (FIG. FIG. 1 ) against wear caused by abrasion / erosion by sand and rock particles as well as by corrosion.
  • the wear protection of the above-mentioned metallic areas by means of a plastic coating for example by means of a shrink tube:
  • a plastic coating for example by means of a shrink tube
  • cover mats or foils which are fixed for example by means of mechanical clamps , or by molded parts.
  • suitable spacers can be attached, which can be realized as sliding nubs on the perforated plate, for example.
  • the materials for the plastic coating are preferably chosen from the group of polyolefins, preferably polyethylene, polypropylene and poly (iso) butylane, since these on the one hand have sufficient resistance to abrasion / erosion and corrosion and on the other hand can be applied as a shrink tube.
  • polyolefins preferably polyethylene, polypropylene and poly (iso) butylane
  • Other possible materials for the plastic coatings or heat shrink tubing are PVDF, Viton, PVC and PTFE.
  • the wall thickness of the shrink tubing is less than 7 mm, typically in the range of 1 to 3 mm.
  • filter module tips 2 are intended to ensure that the extraction of oil, water and gas mixtures or their individual components from the deep well always via the filter modules runs and the existing sand in the borehole is retained on the filter module.
  • filter module tip can be reopened or disconnected if necessary. This is possible, for example, via the blowing off of the filter module tip. Often lances are also used, which are introduced through the interior of the sand filter modules and push out the filter module tip with great force.
  • Filter module tips are preferably designed with a shock-elastic material.
  • the prior art often uses metallic materials. But are also particularly suitable polymer materials, preferably highly elastic polymer materials, which allow an effective reduction of shock loads. Due to their high elasticity and the associated low hardness, all these materials are exposed to a strong abrasive erosion by sand or rock particles.
  • filter module tips with increased abrasion protection are preferably used in combination with ceramic sand filter modules. This can, for example, via the insertion of a wear protection plate 57 ( FIG. 10 ) can be realized in the filter module tip.
  • the wear protection plate is made of a brittle-hard material, preferably made of the same material as the rings. After abrasion of the soft tip in the conveying operation, the wear protection plate prevents further abrasive abrasion by sand or rock particles.
  • the filter module tip can also be manufactured with a wear protection core made of brittle-hard material.
  • the tip must be provided with a preferably polymeric protective layer for cushioning impacts during drilling downhole.
  • FIG. 10 A preferred embodiment of the filter module tip 2 with increased abrasion protection is in FIG. 10 described. It is designed as a solid material and consists essentially of two areas. In the rear, the sand filter module facing area, it has the shape a cylinder; in the front it runs to a point. In the transition of the two areas, a circumferential groove 58 for receiving a snap ring 56 is formed.
  • the filter module tip is pressed into the coupling element via this snap ring.
  • the attachment to the coupling element can also be realized via a snap connection or via shrinking.
  • the wear protection plate 57 is preferably not completely cylindrical in the embodiment suitable for ceramics, but tapering towards the filter module tip. So it can be fixed via a cone / cone connection 52 in the coupling element. To increase the stability of the attachment, a sealing ring 55 can run between the wear protection plate and the groove 53 of the coupling element. In addition, there is a spacer ring 59 between the wear plate and the clamping elements, which prevents the wear plate can bounce against the clamping device in shock loads. This construction allows not only a simple assembly and the ejection of the tip by pressure surge or lance. About the size of the cone angle, the extrusion force can be varied.
  • the wear protection plate can also be fixed with a shape-cut through explosive or O-ring.
  • filter module tip and coupling elements can also be combined.
  • multi-ply filter fabrics are common and necessary for protecting the fine filter.
  • the multi-layer fabric arrangement increases the flow resistance.
  • Multi-ply fabrics also tend to become clogged by the deposition of sands in the cavities, and thus to further increased flow resistance.
  • the ceramic sand filter modules according to the invention can be designed in one layer and be charged directly with the flow.
  • a construction can be selected as a multi-layer filter.
  • a second filter element can be introduced between the tensioning tube and the ring stack.
  • This secondary filter can be designed according to the prior art as a wire mesh, wire winding, slot filter, filter sand packing or for Feinstfilterung as a filter fabric.
  • a variant with an inner second ring stack made of brittle-hard materials can also be integrated into the construction.
  • the clamping tube itself can assume a secondary filter function with a corresponding design, for example, slotted tube or wire mesh.
  • the experiments were carried out by means of a sandblasting machine.
  • the blasting media used were four different proppants typically used in offshore drilling: (1) 100 mesh frac sand, (2) 16/20 mesh frac sand, (3) 20/40 mesh frac sand, (4) 20/40 Mesh Frac Sand High Strength.
  • the jet pressure was 2 bar and the jet duration 2 hours, the jet was quasi point-like applied at an angle of 90 ° to the surface. Depth and the width of the jet impression characterize the erosive wear (see Table 1).

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  • Life Sciences & Earth Sciences (AREA)
  • Engineering & Computer Science (AREA)
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  • Mining & Mineral Resources (AREA)
  • Chemical & Material Sciences (AREA)
  • Dispersion Chemistry (AREA)
  • Physics & Mathematics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Fluid Mechanics (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Filtering Materials (AREA)

Claims (27)

  1. Dispositif de séparation pour la séparation de particules de sable et de roche qui convient en tant que partie intégrante d'un équipement de transport pour transporter des liquides ou des gaz de forages profonds, sachant que le dispositif de séparation comprend au moins un module de filtre céramique (1), sachant que le module de filtre (1) comprend
    a) une pile annulaire (6) de disques annulaires (7) durs et cassants, dont la face supérieure (16) présente au moins trois bossements (8) répartis uniformément sur la circonférence des disques, sachant que les disques (7) sont empilés et serrés de manière à laisser respectivement entre les disques (7) une fente de séparation (9) pour séparer les particules de sable et de roche,
    b) un élément d'accouplement (10) à l'extrémité supérieure et un élément d'accouplement (11) à l'extrémité inférieure de la pile annulaire (6),
    c) un dispositif de serrage (14, 15) pour le serrage axial de la pile annulaire (6),
    d) une cage extérieure (5) pour la protection mécanique du module de filtre (1),
    e) un élément de couplage (12) à l'extrémité supérieure et un élément de couplage (13) à l'extrémité inférieure du module de filtre (1) pour relier le module de filtre (1) à d'autres composantes de l'équipement de transport.
  2. Dispositif de séparation selon la revendication 1, dans lequel les disques (7) sont empilés et serrés dans la pile annulaire (6) de manière à être mobiles l'un contre l'autre dans le sens radial et tangentiel.
  3. Dispositif de séparation selon la revendication 1 ou 2, dans lequel le dispositif de serrage comprend des tiges de serrage (14) disposées à l'intérieur de la pile annulaire (6).
  4. Dispositif de séparation selon la revendication 1 ou 2, dans lequel le dispositif de serrage comprend un tube de serrage (15) disposé à l'intérieur de la pile annulaire (6).
  5. Dispositif de séparation selon au moins l'une des revendications précédentes, celui-ci comprenant en outre une ou plusieurs enveloppe(s) de protection (4).
  6. Dispositif de séparation selon au moins l'une des revendications précédentes, celui-ci comprenant en outre à l'extrémité inférieure, une pointe de module de filtre (2) ayant une protection accrue contre l'abrasion.
  7. Dispositif de séparation selon au moins l'une des revendications précédentes, dans lequel les bossements (8) sur la face supérieure (16) des disques (7) ont la forme de segments sphériques.
  8. Dispositif de séparation selon au moins l'une des revendications 1 à 3 et 5 à 7, dans lequel les disques annulaires (7) présentent au moins trois évidements (20) sur leur surface d'enveloppe intérieure, qui servent à recevoir les tiges de serrage (14).
  9. Dispositif de séparation selon au moins l'une des revendications précédentes, dans lequel les disques annulaires (7) présentent au moins trois renfoncements (21) dans leur face inférieure (18) dans lesquels les bossements (8) peuvent être positionnés.
  10. Dispositif de séparation selon au moins l'une des revendications précédentes, dans lequel la face supérieure (16) des disques annulaires (7) est conçue perpendiculairement à l'axe des disques.
  11. Dispositif de séparation selon au moins l'une des revendications précédentes, dans lequel la face inférieure (18) des disques annulaires (7) est conçue inclinée vers l'extérieur ou vers l'intérieur, de préférence inclinée vers l'intérieur, et de préférence concave.
  12. Dispositif de séparation selon au moins l'une des revendications précédentes, dans lequel l'épaisseur de paroi radiale des disques annulaires (7) mesure au moins 2 mm, de préférence au moins 5 mm.
  13. Dispositif de séparation selon au moins l'une des revendications précédentes, dans lequel l'épaisseur des disques annulaires (7) mesure entre 1 et 20 mm, de préférence entre 1 et 10 mm.
  14. Dispositif de séparation selon au moins l'une des revendications précédentes, dans lequel la fente de séparation (9) entre les différents disques (7) présente une hauteur de 0,05 à 1 mm, de préférence de 0,05 à 0,5 mm.
  15. Dispositif de séparation selon au moins l'une des revendications précédentes, dans lequel le matériau dur et cassant des disques annulaires (7) est sélectionné parmi des matériaux céramiques oxidiques ou non-oxidiques, des céramiques mixtes constituées de ces matériaux, des matériaux céramiques avec un ajout de phases secondaires, des matériaux mixtes avec des parts de matériaux durs céramiques et avec une phase liante métallique, des matériaux de fonte durcis par précipitation, des matériaux de la métallurgie des poudres avec des phases dures formées in-situ, et des matériaux céramiques renforcés de fibres courtes et/ou longues.
  16. Dispositif de séparation selon au moins l'une des revendications précédentes, dans lequel les matériaux durs et cassants des disques annulaires (7) possèdent des valeurs de dureté HV ≥ 15 Gpa, de préférence ≥ 23 Gpa.
  17. Dispositif de séparation selon au moins l'une des revendications précédentes, dans lequel les matériaux durs et cassants des disques annulaires (7) possèdent des modules d'élasticité ≥ 200 Gpa, de préférence ≥ 350 Gpa.
  18. Dispositif de séparation selon au moins l'une des revendications précédentes, dans lequel les matériaux durs et cassants présentent une densité d'au moins 90%, de préférence d'au moins 95%, de la densité théorique.
  19. Dispositif de séparation selon au moins l'une des revendications précédentes, dans lequel le matériau dur et cassant est du carbure de silicium (SSiC) fritté ou du carbure de bore.
  20. Dispositif de séparation selon au moins l'une des revendications précédentes, dans lequel, dans leur surface périphérique extérieure, les éléments d'accouplement (10, 11) présentent au moins une rainure périphérique (22) destinée à recevoir une bague d'étanchéité (23).
  21. Dispositif de séparation selon au moins l'une des revendications précédentes, dans lequel le diamètre extérieur des éléments d'accouplement (10, 11) est égal ou supérieur à celui des disques annulaires (7).
  22. Dispositif de séparation selon au moins l'une des revendications précédentes, dans lequel les éléments d'accouplement (10, 11) sont fabriqués à partir du même matériau dur et cassant que les disques annulaires (7).
  23. Dispositif de séparation selon au moins l'une des revendications précédentes, dans lequel les dispositifs de serrage (14, 15) comprennent en outre un jeu de serrage, comprenant un manchon de serrage (26), des ressorts de pression (27) et des écrous de serrage (28) pour les tiges de serrage (14) ou des bagues de serrage (29) pour le tube de serrage (15).
  24. Dispositif de séparation selon au moins l'une des revendications précédentes, dans lequel les tiges de serrage (14) ou le tube de serrage (15) sont fabriqués en acier, de préférence en acier résistant à la corrosion.
  25. Dispositif de séparation selon au moins l'une des revendications précédentes, dans lequel les éléments de couplage sont fabriqués en acier, de préférence en acier résistant à la corrosion.
  26. Dispositif de séparation selon au moins l'une des revendications précédentes, dans lequel la cage extérieure est fabriquée en tant que crible à grosses mailles ou en tant que tôle percée et est fabriquée de préférence en acier, de préférence encore en acier résistant à la corrosion.
  27. Utilisation d'un dispositif de séparation selon au moins l'une des revendications précédentes pour la séparation de particules de sable et de roche dans un procédé pour le transport de liquides ou de gaz de forages profonds ou de la roche.
EP10715683.8A 2010-03-31 2010-03-31 Dispositif de séparation résistant à l'usure pour la séparation de particules de sable et de particules de roche Active EP2553216B1 (fr)

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EP (1) EP2553216B1 (fr)
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AU (1) AU2010350079B2 (fr)
BR (1) BR112012024771B1 (fr)
CA (1) CA2738171C (fr)
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CA2738171C (fr) * 2010-03-31 2016-05-17 Esk Ceramics Gmbh & Co. Kg Dispositif de separation resistant a l'usure pour extraire le sable et les particules de roche

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MX2012011373A (es) 2012-11-30
CA2738171C (fr) 2016-05-17
US20120018146A1 (en) 2012-01-26
BR112012024771B1 (pt) 2019-07-02
ES2462116T3 (es) 2014-05-22
BR112012024771A2 (pt) 2016-06-07
EA022124B1 (ru) 2015-11-30
EP2553216A1 (fr) 2013-02-06
US8662167B2 (en) 2014-03-04
AU2010350079B2 (en) 2014-10-09
CN102822444B (zh) 2016-02-24
CN102822444A (zh) 2012-12-12
AU2010350079A1 (en) 2012-10-18
CA2738171A1 (fr) 2011-09-30
DK2553216T3 (en) 2014-03-03
EA201290987A1 (ru) 2013-03-29
WO2011120539A1 (fr) 2011-10-06

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