NO20220791A1 - Mechanical Casing Annulus Packer II - Google Patents
Mechanical Casing Annulus Packer II Download PDFInfo
- Publication number
- NO20220791A1 NO20220791A1 NO20220791A NO20220791A NO20220791A1 NO 20220791 A1 NO20220791 A1 NO 20220791A1 NO 20220791 A NO20220791 A NO 20220791A NO 20220791 A NO20220791 A NO 20220791A NO 20220791 A1 NO20220791 A1 NO 20220791A1
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- Prior art keywords
- ring
- expanding
- packer
- casing
- rings
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Classifications
-
- E—FIXED CONSTRUCTIONS
- E21—EARTH DRILLING; MINING
- E21B—EARTH DRILLING, e.g. DEEP DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B33/00—Sealing or packing boreholes or wells
- E21B33/10—Sealing or packing boreholes or wells in the borehole
- E21B33/12—Packers; Plugs
- E21B33/1208—Packers; Plugs characterised by the construction of the sealing or packing means
- E21B33/1216—Anti-extrusion means, e.g. means to prevent cold flow of rubber packing
Description
Introduction
The present invention relates to a mechanical compression casing annulus packer for being arranged between a surrounding casing pipe and a pipe string which comprises the mechanical casing annulus packer of the invention. The mechanical casing packer of the present invention may be used for several tasks:
- for permanently setting a packer between a liner pipe and a casing pipe in a well;
- for use in completion of a well under construction, setting and sealing a completion in a production liner;
- for setting a packer between a patch liner pipe and a casing pipe,
and other mechanical constellations wherein a permanent seal is required between a casing pipe section of a given diameter, such as 95/8 '' and a surrounding casing pipe section of a subsequent larger diameter such as 133/8'', or for sealing a 133/8'' casing in a 185/8'' casing. The casing packer assembly of the present invention may also be used as the sealing arrangement of a bridge plug or retrievable bridge plug.
The purpose of the present invention is to provide a mechanical set annulus packer packer for being permanent, wherein a permanent seal is formed between a casing pipe section and a surrounding casing pipe section, wherein the seal shall be gas tight according to a standard such as V0. The seal must withstand a high pressure of e.g. more than 443 Bar or 6425 psi, or even up to 690 Bar or 10000 psi, and the packer must endure standing in a chemically aggressive environment of H2S-containing fluids such as water, oil, natural gas, drilling mud, Sulphur Oxides, and abrasive particles such as sand. The temperature in the well is elevated both due to the geothermal gradient and due to well processes and may be up to 170 Deg. C. The sealing effect is required to hold for a very long time, many years such as up to 100 years in order to prevent undesired petroleum or water leakages now and far into the future.
Brief Figure captions
The present invention and related background art are shown in the attached drawing Figures, wherein
Fig.0a: illustrates an ISO 14310:2008, grade V0 performance test envelope. The pressure is exerted on a sealed mechanical casing annulus packer, wherein the context illustrated for each quadrant. Pressure P is on the horizontal abscissa and force F on the mechanical casing annulus packer is along the vertical ordinate. Max pressure is 137.9 Bar =2000 psi. Max pull is 136.2 metric tonnes. The max push and pull are almost symmetrically used in all four quadrants; the max push is - 113.5 metric tonnes. The force and the pressure on the sealed mechanical casing annulus packer illustrated in each quadrant is as follows:
Fig.0b: illustrates a higher pressure standard: ISO 14998:2015, grade V0 performance test envelope. The pressure is exerted on a sealed mechanical casing annulus packer as illustrated in each quadrant in Fig.0a. The pressure P range here is more severe; minus 274.1 Bar (P from above) to plus 442.8 Bar or 6425 psi (P from below), The max push F and pull F are the same above: plus 136.2 metric tonnes (pull) to minus 113.5 (push).
Those are the testing force and pressure limits for the two tests. The test temperature range is 20 degs.C. to 130 degs.C.; the test gas is Nitrogen.
In the below description, the casing packer is a 135/8 '' Ø to be set in 17'' inner Ø in a 185/8 casing.
Fig.1 shows an annotated photograph of a packer end element showing damage to part of the packer cross section, during testing of an early, unsuccessful embodiment of an expanding ring. Please notice the part-spheroidal faulting having propagated inwardly from the destroyed, part extruded edge, and the granular bottom of the remaining cavities near the edge.
Fig.2 is another example of an unsuccessful test of a packer end element ring with damage craters arisen during pressure testing, presumably due to mechanical disintegration and extrusion of the packer end element ring. Please notice the spheroidal-like fault formation of craters extending stepwise in along the external cylindrical surface, and the granular like remaining bottom of the craters formed. One may suspect extrusion radially above the supporting expanding steel ring, and/or high-pressure gas flow leakage across the edge.
Fig.3 comprises drawings of an early, unsuccessful attempt of a so-called "backup ring", i.e. an expanding ring as further shown in the picture of the tested version of Fig.4 below. The expanding ring of Fig.3 could have been arranged in a casing annulus packer otherwise shown in Fig.6a, but is not applicable because it fails, please see details why, described under reference to Fig.4 and Fig.5. Upper left is a plane view of what we call the front of the expanding ring, it comprises a 6.7 mm deep notch of 120 degrees opening and made with an angle relative to the radial line, then a cut slit with 7 degrees angle relative to the frontal plane down to a distance of 118.5 mm wherein a straight cut out of 11.5 mm is made to the rear surface of the expanding ring. The front will face a ring-shaped outer part of a packer ring's planar rear surface when axially compressed. The conical inner part of the front will climb on a relatively steep 60 deg. angled corresponding conical rear face of an inner ring, which front again is planar and engages a ring-shaped radially inner portion of the planar rear surface of the packer ring.
Fig.4 is an annotated photograph of a third tested, failed packer element end ring to the left, with clearly visible damage about its portions facing the notch expanded portion of an expanded and deformed, failing expanding ring of the kind drawn in Fig.3 above. Also seen is an underlying wedgeshaped inner ring, an inner ring for supporting the so-called "backup ring", i.e. the expanding ring, which enables the expanding ring to expand radially and climb radially in order to support the packer end element with its ring-shaped planar outer surface facing the packer end element. These rings have been tested on a cylindrical mantle testing device in a larger-bore casing test section.
In Fig.4; please observe that the peripheral extent of deep damage in the packer element end ring generally overlaps and exceeds the expanded notch portion length along the base tongue of the expanded expanding ring.
Fig.5 is an enlarged part corresponding to the rectangle indicated in Fig.4. Please notice that in the photograph the components are only placed loosely in their mutual rotationally correct positions, they are not assembled under compression in the image. Please notice that the extent of general damage of the packer element end ring may be crudely subdivided into three parts with generally decreasing severity as counted from the original notch position.
Fig.6 shows drawings of a pre-set casing annulus packer according to an embodiment of the invention. All relative movements to be made are indicated by sinistral / dextral arrow pairs.
- top: an end view and a lateral view.
- an axial section view and partial view of the casing annulus packer.
- in the middle, enlarged details of packer element end rings (16) and expanding rings (28) before axial compression and radial expansion; and to the left a set of slips (5) which will expand and engage first when the assembly is axially compressed.
- a ratchet lock ring detail between the sliding sleeve and an actuator sleeve.
- at the bottom of the sheet, force transfer keys connecting the tool-engageable sliding inner sleeve with the external actuator sleeve.
Fig.6b shows drawings corresponding to Fig.6a, but in the set state of the casing packer assembly.
Fig.7a and Fig.7b illustrate a first embodiment of an expanding ring according to an embodiment of the invention, please also see Fig.8a. In this embodiment, the expanding ring (28) is made in one solid piece of steel.
Fig.8 is a detailed longitudinal section of casing packer seal assembly according to the invention, before set and after set. (packer shortening not taken into account in this drawing). In the upper part of the sheet the ready-for-set casing packer seal assembly, and in the lower part of the sheet the same casing packer assembly is shown in its set position, wherein a moving ratchet housing or similar is forced in from below by a tool, and the expanding rings (28) and the packer end elements (16) have been expanded and seal against the surrounding casing wall (only shown in the lower part of Fig.8).
Figs.8a, 8b, and 8c illustrate three different embodiments of an expanding ring and packer assembly of the invention, in their ready state and in their set state. Fig.8a shows a cross-section of the solid ring assembly corresponding to Fig.7a and Fig.7b, and Fig.8.
Fig.8b shows a cross-section of an embodiment of the expanding ring (28) with two internal expanding rings, corresponding to what is shown in Fig.9a and Fig 9b, and is a principle longitudinal section of second embodiment of a casing packer seal assembly before set and after set.
Fig.8c shows a cross-section of an embodiment of the expanding ring (28) with a conical stack of three frontal expanding disc rings (28d1, 28d2, 28d3) ahead of the base expanding ring, all three expanded together with the packer element end ring (16) due to the compression force.
Fig.9a illustrates a longitudinal section along an embodiment of the casing packer seal assembly of the invention wherein the expanding ring (28) is designed according to the second embodiment of the expanding ring (28) corresponding to Fig.8b and corresponding to the below Fig.9b.
Fig.9b illustrates a perspective view of an expanded gap formed in the base expanding ring part of the above mentioned second embodiment of the expanding ring, the internal expanding ring omitted from the view. Note the overlap of the tip of the arc-shaped expanded tongue (28te) and the base portion of the shoulder portion (28bs) contributing to this fully expanded ring is not collapsing axially under axial load.
Fig.9c illustrates the embodiment of the expanding ring assembly with the expanding ring (28) with two internal expanding rings (28ai, 28bi), all arranged between an inner cone ring (7) for facing the packer end element (16), and an outer cone ring (6), the two cone rings for axial forced radial expansion of the packer seal rings. A corresponding expanding ring assembly is to be arranged opposite the expanding ring(s) (28).
Fig.10 is a perspective of an expanded ring of the embodiment shown in Fig.9c, and an enlarged portion of the gap-forming portion showing the arc-shaped recess bottom which will be forced against the packer end element (16) plane outer rim portion (16o) (part of which will be deformed into the recess). The recess here has bevelled ramp surfaces against the packer end element, and it is rather shallow, so the deformation bulge-out of the outer rim portion (16o) into the groove is so small that rupture deformation of the packer end element (16) is avoided. The straight gap at the rear portion of the expanding ring is of less significance, where metal meets metal unless in the gap, which is mechanically supported across the dual internal expanding rings (28ai, 28bi).
Fig.11 is an embodiment of the invention, showing a third embodiment of the expanding ring (28) comprising a rear conic base ring (28Y) and including a fore, internally conic, stack of three discs (28d128d2 , 28d3) which are fixed together at one point with the base ring, all in an un-expanded state. Each disc (28d1, 28d2, 28d3) has a cut gap for being expanded. The radially slimmest disc (28d3) may have a notch (28n) forming the slit / gap (28g1) which forms part of through slit (28s).
Fig.12 is a cross-section of the same expanding ring (28) as shown in Fig.11.
Background art
A drill pipe string conveyed running tool is required for setting the packer of a large-bore casing section in the present context. The running tool has an external dog key profile which fits in an internal ring-shaped lock profile of a corresponding internal setting sleeve in the packer casing section. The ring-shaped lock profile is connected via radial connections pins through slits in the static packer casing section body, the radial connecting pins holding a compression setting sleeve which is pushed upwardly to compress and thus expand the packer to engage with and seal against the surrounding casing pipe's inner wall.
A general problem is to avoid unnecessary deformation of the packer during setting, and also later deformation, both due to extrusion of the packer material through the annular gap between the packer casing section and the surrounding casing section, or through internal pathways in the compression setting mechanism. Another problem is to avoid leakage of the packer.
Traditional packer end element rings have a problem during axial compression the disadvantage of extrusion of the packer end element ring in an unsupported radial ring surface portion of the packer end element ring through a radial gap between outside of a compression ring and the surrounding casing section wherein the packer is sealing. The result is that the entire packer end element ring cracks up, becomes granularly eroded and loses its sealing effect. The consequence is that such a packer end element ring may have compression pressure limits that do not meet the practical or safety requirements for sealing off an annulus of a casing portion within a larger casing portion. Low sealing pressure may result in leakages and erosion which incurs accelerating leakages.
Packers and related expansion rings are described in US 4765404 A, US 2012/0187632 A, US 2003/0079887 A, US 3559733 A, and WO 2018/056951 A.
US 4765404 A describes a packer device set by axial compression, please see Fig.10, for expansion against a surrounding casing. The packer end element slides along a cylindrical mandrel. the packer comprises:
- an outer ring-shaped packer end element with an axially outward facing radially inner and outer plane ring face,
- first and second conical inner rings have an axially inward facing ring surface against the packer end element in its expanded state,
- first and second expansion rings (112) having a ramp face for climbing and expanding on the conical rings,
- the first and second expansion rings have a plane, radially outer ring face for engaging and expanding with the outward facing ring face of the packer end element, so as for preventing extrusion.
US 2012/0187632 A describes an expansion ring for preventing extrusion of the packer end element. The expansion ring comprises a number of slanted segments which form a mutual partition range which allows radial expansion under weight load.
A compression ring may be split in order to make an expanding compression ring which expands during axial compression supports the packer end element ring further out in order to reduce such an external radial gap, and further supporting the split ring and the radially inner face ring portion of the packer end element ring.
An orthogonally cut split ring will expand easily, however the gap will not support the expanding packer end element ring and will incur an extrusion through the rectangular gap formed in addition to opposite shear deformation on either side of the gap, and will easily ruin the packer through extrusion and in shear deformation even under low mechanical force axial pressure during setting.
A further development, a short slant cut expansion ring will also incur a single-side shear deformation and extrusion. This creates a large oblique ramp of which one portion intrudes into the packer end element during compression and resulting expansion, further initiating a shear deformation and damage, and opens for extrusion, and is only marginally less severely affecting than a straight cut expansion ring.
Problems related to background art and development
In further attempts to solve the problems of deformation of the axial compression packer end element, a low-angle slit dual bridge expanding ring combined with a wedge shaped backup ring supporting the radially outer and inner ring surfaces of the expanding packer end element, as shown in the technical design drawing of Fig.3 (un-deformed, un-damaged), and rendered as a post-test picture in Fig.4.
Fig.1 and Fig.2 show damaged packer end elements resulting from tests earlier than the one shown in Fig.4.
Now back to Fig.3: The drawing shows an expansion ring made in a failed attempt to overcome the above-mentioned problems. An expansion ring of height 24.3 mm and Ø 298.5 mm is split between a 6.7 mm deep, 120 degrees blunt notch across one portion of the ring, followed by a 118.5 mm long expansion slit, 7 degrees oblique, falling off 4.1 mm to an orthogonal slit out of the opposite surface. The low fall-off of 4.1 mm and the oblique, 6.7 mm shallow slit was thought to render little extrusion and little granular erosion of the packer. Despite this attempt, it failed, as seen in the images taken after disassembly of the tested packer assemblies.
Fig.4 shows an image of a packer element end ring, damage to part of the packer profile, and (to the right) an expanding ring used during the setting and compression of the packer element end ring, which is expanded and deformed during the axial compression setting of the packer. Also seen inside the left portion of the expanding ring and facing the end element packer's flat ring-shaped face, is a wedge-shaped backup ring which forms a radially inner ring face which together with the outward climbing, radially outer ring face of the expanding ring, compresses the packer element in the axial direction.
In Fig.4, the 120 degrees wide notch has expanded along the slit to two 30 degrees ramps, both 6.7 mm high, and the base straight slit cut portion in the rear plane has opened up, while facing away from the packer. In the image the expansion of the ring is about 75 mm along the low-angle slit. It can be seen that the packer-adjacent tongue of the expanding ring has bent at its bae near the straight gap. There is a damage range affecting nearly half the thickness of the packer end element, the damaged range being near and adjacent to the expanded notch portion length along the base tongue of the expanding ring. This is further analyzed in the subsequent Fig.5.
Fig.5 is an enlarged part corresponding to the rectangle indicated in Fig.4. Please notice that in the photograph the components are only placed loosely in their mutual rotationally correct positions, they are not assembled under compression in the image. Please notice that the extent of general damage of the packer element end ring may be crudely subdivided into three parts with generally decreasing severity as counted from the original notch position:
- firstly, a left range of deeper extrusion and / or granular bottomed erosion about the position of the original, un-expanded notch. We assume that extrusion of the packer element end ring may have started here, expanding into the notch and being subject to high relative tensile stress and shear stress, and possibly later subject to high pressure gas passage erosion.
- secondly, a middle range of less deep extrusion and / or transverse crack-controlled exfoliation which may have occurred as the packer has been extruded in the wider gap across the now exposed base tongue of the expanding ring. We assume that the expanding ring has some hysteresis after being released and may have partly closed from its widest gap; the base tongue exposed gap may have been wider than when photographed. Part of the deformation in this range and in the crack behind may indicate dextral deformation which may be due to the dextral shear exerted by the right-hand movement during expansion of the steel tongue.
- thirdly, an end range of shallower, granular edge erosion decreasing into no erosion. Small lugs or tongues bent in the same direction along this edge interface indicate dextral shear in addition to the granular erosion. We also see that the tongue is deformed near this end range which contributes to reduced steel support of the polymer ring in this region.
Generally, we interpret the damage of the packer end element ring to be due to, first, extrusion deformation and gas leakage erosion near the notch; secondly, shear deformation and extrusion and gas leakage erosion along the widening notch gap, and third, shear deformation and some gas leakage erosion along the remainder affected portion.
Brief summary of the invention
The invention provides a solution to the above-mentioned problems. The invention is a casing packer seal arrangement, comprising
- a sliding casing packer seal assembly arranged for being set by axial compression to expand against a surrounding casing, said casing packer seal assembly being compressed and sled along a cylindrical mandrel. The casing packer seal assembly comprises:
- at least one packer end element ring having mutually opposite, axially outward facing radially inner and outer plane ring portions;
- first and second conical inner rings having an axially inward directed plane ring face abutting said packer element end rings' inner plane ring portions in their expanded state; - first and second expanding rings each having a conical ramp face
for climbing, thus expanding, on said conical inner rings;
- said first and second expanding rings each having a plane, radially outer ring face for engaging, expanding with and supporting said packer element end ring's axially outward facing plane ring portions;
so as for when expanded, preventing extrusion of said so expanded packer element end ring in an annulus gap between said expanding rings and a surrounding casing pipe.
The invention is defined in claim 1. Further embodiments are defined in the preceding claims, and are described in the below description of embodiments of the invention
Description of embodiments of the invention
Below, the invention and embodiments of the invention are described. The invention is casing packer seal arrangement, please see Fig.8, Fig.8a, Fig.8b, and Fig.8c. See also Fig.9a.
The invention comprises several technical features, including a sliding casing packer seal assembly (100) arranged for being set by axial compression to expand against a surrounding casing. This casing packer seal assembly (100) is arranged for being compressed and sled along a cylindrical mandrel (24) between a position ready to set, and a compressed position when the packer seal assembly is set.
For the position ready to set, please see Fig.8, upper part; Fig.8a, upper part; Fig.8b, upper part; Fig. 8c, upper part; and Fig.9a.
The casing packer seal assembly (100) comprises:
First, at least one packer element ring (16) having mutually opposite, axially outward facing radially inner and outer plane ring portions (16o, 16i, 16o, 16i), please see Fig.8, upper and lower part of the sheet; Fig.8a, lower part of the sheet, wherein the outer plane ring portion surface (16o) of packer (16) is compressed and radially expanded against the expanded arch-shaped tongue (28te) of the expanding ring (28), and the inner plane ring surface (16i) is compressed and encountered by the inner plane ring surface of the conical inner ring (7). Please also see the same effect using the other embodiments shown in Fig.8b, lower part, and in Fig.8c, lower part.
Second, the casing packer seal assembly (100) comprises: first and second conical inner rings (7, , 7r, 7, 7r) having an axially inward directed plane ring face (7i, 7i) abutting said at least one packer element end rings' (16, 16) inner plane ring portions (16i, 16i) in the expanded state, please see Fig. 8a, lower part; Fig.8b, lower part; and Fig.8c, also lower part.
Third, the casing packer seal assembly (100) comprises: first and second expanding rings (28, 28) each having a conical ramp face (28i, 28i) for climbing, thus expanding, on said conical inner rings (7, 7); said first and second expanding rings (28, 28) each having a plane, radially outer ring face (28o, 28o) for engaging, expanding with and supporting said packer element end ring's (16, 16) axially outward facing plane ring portions (16o, 16o). Please see Fig.8a, lower part; Fig.8b, lower part; and Fig.8c, lower part.
The effect of using the above parts is, so as for when the expandable portions of the casing packer seal assembly have been compressed and expanded, they will prevent extrusion of the so expanded packer element end ring (16, 16) in an annulus gap between the expanding rings (28, 28) and a surrounding casing pipe.
In practice, the casing packer assembly is axially dual-sided as illustrated in Fig.6a, Fig.6b, and Fig.8, and particularly the arrangement of the packer end element (16) with a bi-conical central element (18, 17), is more elaborate than the single packer element (16) shown in Fig.8a, Fig.8b, and Fig.8c.
Direction definitions:
In defining directions of the casing packer seal assembly (100), we will artificially imagine an origin in the axial direction. The middle plane of the casing packer assembly (100) is imagined, please see Fig. 8, in the middle axial transverse plane of the bi-conical central element (18, 17). The casing packer assembly is to a wide extent, in practice out to the outer rings (6), except for minor details, axially symmetrical about this middle plane. (The middle plane thus moves during compression and setting). The direction of "Axially inward" is everything facing in a direction towards this middle plane. The direction of "Axially outward" is counted for everything facing in a direction away from this middle plane of the middle, bi-conical central element (18, 17). Onto this bi-conical element, in an embodiment of the invention, both expandable packer element end rings (16) (of "rubber", TFE/P) will ramp up and mutually move towards each other when axially compressed. Please note in Fig 8 that the middle plane of this assembly will itself translate axially, during the compression because the active ratchet housing (10) (shown coming in from the right side which is from below when in a well) will compress from one side and push the assembly to the left side in the drawing, towards a fixed point ultimately, regardless of whether there are casing slips or not.
In such an embodiment, said packer element (16) is arranged as follows, please see Fig.6a, Fig.6b, and Fig.8:
- first and second packer element end rings (16, 16) have mutually opposite axially outward facing plane outer and inner ring portions (16o, 16i, 16o, 16i), respectively,
- wherein the first and second packer element end rings (16, 16) each have an axially inward directed conical ramp portion (16r, 16r), and
- there is arranged a middle, bi-conical central element (18, 17) for ramping out the first and second packer element end rings (16, 16).
In an embodiment there is arranged a sealing O-ring (26) between the two facing portions of the opposite bi-conical central element (18, 17) and also a sealing O-ring (25) under the bi-conical central element (18, 17), sealing against the cylindrical surface of the mandrel (24), please see Fig.8.
In an embodiment of the invention shown in Fig.8, 12. The casing packer seal arrangement (100) further comprises that said sliding casing packer seal assembly (100) is arranged for being set by axial compression between a sliding, moving ratchet housing (10) , and an axially opposite arranged, slips ring (8) which may be considered static relative to the moving ratchet housing (10), please see Fig.8, and in a smaller scale, in Fig.6a and Fig.6b. In an embodiment of the invention the slips ring (8) is actually itself also sliding, and sliding towards slips (5) and ultimately against a fixed slips end ring (23) on said mandrel (24), please see Fig.6b for the set state of both packer and slips, and in Fig.6a for the pre-set state. In such an embodiment of the invention, the casing packer seal arrangement is combined on the same mandrel (24) with wedge-based slips (5) arranged to be forced out by the conical slips ring (8) and the oppositely arranged slips end ring (23).
As shown in the embodiments such as shown in Fig.6a, Fig.6b, Fig.8, Fig.8a, Fig.8b, Fig.8c, and in Fig.9a, the casing packer seal arrangement may have further components to promote the expansion which are also advantageous in order to limit undesired radial expansion of the expanding ring: In such embodiments there are arranged first and second conical outer rings (6, 6), wherein the conical outer rings are arranged between an axially outward facing conical, radially expanding ramp face (28r, 28r) of said expanding rings (28, 28), and said moving ratchet housing (10) on the one axial side and said (relatively static) slips ring (8) on the axially opposite side. Correspondingly, in the embodiment the conical outer rings (6, 6) have an axially inward facing conical ramp (6ri, 6ri) for expanding the axially outward facing conical ramp (28ro) of said expansion ring (28), please see Fig. 8a, and the same feature is shown in Fig.8b and Fig.8c. This feature promotes the radial expansion of the expanding ring (28). In an embodiment the conical outer rings (6, 6) could have been manufactured as integrated portions on the ratchet housing (10) and the slips ring (8), respectively, in order to reduce the number of components.
In an embodiment in order to limit radial expansion, the axially inward facing conical ramp (6ri) of said outer ring (6) is provided with a radially outer limiter rim (6oL) arranged for outer limiting the radial expansion of a corresponding radially inner limiter rim (28iL) of said axially outward facing conical ramp (28ro) of said expanding ring (28). Those, during compression, radially abutting limiter rims (6oL) and (28iL) are advantageous to have in order to avoid uncontrolled radial expansion of the expanding ring, whereby the expanding ring otherwise would collapse outwardly and axially in the annulus if not restricted radially.
In an embodiment of the invention as described in any of the preceding paragraphs, the casing packer seal arrangement may further comprise:
- said sliding, moving ratchet housing (10) having an internal ratchet ring (10r), please see Fig.6a, the ratchet ring (10r) arranged for locking said rathcet housing (10) when in its axially compressed position, locking it against corresponding external ratchet threads (24R) on said mandrel (24), preventing reversal and unloading of the compression of the casing packer seal arrangement.
The ratchet threads (24R) may be ring threads if absolutely permanent ratchet locking. But in an embodiment the ratchet threads (24R) may also be screw threads if the casing packer shall be used in a re-settable packer such as in a retrievable bridge plug. For using the present packer seal assembly (100) in a retrievable bridge plug instead of a casing packer, the mandrel may be rotated in order to unscrew the ratchet lock. Otherwise, if first set, it cannot be unset. This is regardless of whether there are slips arranged or not, but it is in practice required to have both packer and slips in a retrievable bridge plug.
It is required to have some force to compress the casing packer assembly (100). One may assume that the external casing such as 133/8'' is fixed in the well, and that a 95/8'' casing with the present packer seal arrangement (100) is placed and held in its desired position for being set. In order for this to be achieved for a casing packer, in an embodiment of the invention said ratchet housing (10) is connected via a set of force transfer keys (4) fixed to said ratchet housing (10) and radially arranged through axially directed force transfer slots (4s) through said mandrel (24) or a packer mandrel (12) or end sub sleeve (2) in the continuation of said mandrel (24), please see Fig.6a and Fig.6b. Those force transfer keys (4) are then connected to a slidable inner sleeve (3) inside said mandrel (24) or said packer mandrel (12) or end sub (1). This slidable inner sleeve (3) is then provided with an internal key profile (3K) for receiving a dog key tool for axial translation of said inner sleeve (3). The dog key tool may then be run on a drill pipe string but it may also be envisaged that it may be run via a well tractor, wireline or rod-conveyed or autonomous, which runs to a position inside mandrel (24), anchors itself inside the mandrel (24) and extends an actuator with the desired dog key profile and moves the slidable inner sleeve (3) to set the casing packer. The dog key tool may also be run in on a conveyed tubing.
Based on the invention and its embodiments described above, we envisage a first, second and third embodiment of the invention's expanding ring (28), of which all embodiments share the following features:
- The expanding ring (28) is provided with a shallow notch (28n) in said radially outer ring face (28o) extending down to a slit path (28s) , please see Fig.7a, and Fig.7b, which slit path (28s) extends in general to an opposite, outward facing rear face (28r) of said expanding ring (28). This will allow peripheral thus radial expansion of said expanding ring (28) along said slit path (28s). As seen from the packer end element's side, the expansion of the expanding ring commences at the shallow notch (28n) and a shallow groove bottom is exposed in the radially outer ring face (28o), allowing only a very limited local, short, arc-shaped axial-directed extension of the packer end element is allowed. In an embodiment of the invention the shallow notch (28n) may have a depth of about 2 - 5 mm; in a preferred embodiment a depth of 3 to 4 mm, and in a most preferred embodiment a depth of 3.2 to 3.8 mm. The above features are also present in the embodiments illustrated in Fig.8, Fig.8a, Fig.8b, Fig.8c, Fig.9a and Fig.9b, Fig.9c, Fig.10, Fig.11, and in Fig.12, although the actual slit path (28s) is of various embodiments in the three variants illustrated.
In an embodiment which is also common to the three embodiments of the expanding ring (28) shown in Fig.8a, Fig.8b, and Fig.8c, is that the slit path (28s) has a shallow, planar slit portion (28sp) beginning from said shallow notch (28n), said planar slit portion (28sp) allowing, during expansion, for a shallow, planar, peripherally widening arc-shaped recess bottom (28B) uncovered between the peripherally widening notch gap's (28n) opposite faces, said planar slit portion (28sp) underlying an arc-shaped tongue (28te) of even thickness along the length of said planar slit portion (28sp). The planar slit portion (28sp) may then have its continuation in various ways through the remainder of the slit path (28s) to the opposite face (28r) of the expanding ring (28).
In an embodiment of the invention these first, second and third embodiments of expanding ring (28) have in common that a peripheral length of said planar slit portion (28sp) and a length of said arcshaped tongue (te) is longer than a maximally allowed peripheral widening of said expanding ring (28), so as for only said, planar, peripherally widening arc-shaped recess bottom (28b) of said slit (28s) to be exposed to said packer end element (16) during expansion.
A significant advantage of this shallow, planar, peripherally widening arc-shaped recess bottom (28B) is the fact that the arc-shaped recess bottom (28b) behind the shallow plane slit (28sp) at 3.0 - 4.0 mm depth along ring surface (28o) generally forms the plane recess exposed towards the packer (16). No further slit gap is exposed to the packer end element (16), thus no extrusion of the outer rim of the packer end element is allowed even under high pressure. The axial extrusion of the ringshaped outer part of the packer end element (16) is then only about 3-4 mm.
Also common to the first, second and the third embodiment of the expanding ring (28) is a further embodiment that the feature of said shallow notch (28n) comprises two facing opposite bevelled surfaces (28nb) , please see Fig.7a, Fig.7b, Fig.9b, and Fig.10 in particular, and that the arc-shaped tongue (28te) comprising one of said bevelled surfaces (28nb) at its end. An advantage of this feature is that there is no sharp edge scraping away along the affected outer planar ring portion (16o) of the packer end element (16), but only a bevelled, low-angle bevelled end portion as the arc-shaped tongue is peripherally moving away during its expansion, and no sharp edge to initiate a cut in the outer planar ring portion (16o) as the pressure is set on the packer end element (16). This reduces the risk of damage to the edge and planar ring portion (16o) of the packer end element (16), and contributes to maintaining the sealing effect of the packer end element.
In an embodiment of the invention, mutually expansion-sliding portions of said expanding ring (28), including at least
- said planar, peripherally widening arc-shaped recess bottom (28B) uncovered between said peripherally widening notch gap's (28n) opposite faces,
- said planar slit portion (28sp) underlying said, and including,
- said arc-shaped tongue (28te),
all are surface covered by a low-friction material such as Tetrafluorethylene (Teflon, TFE), Molykote (R) D321R, Xylene, silicone grease, or similar means withstanding a temperature of up to 170 deg. C or even up to 260 deg. C.
There are several advantages to this embodiment: It reduces the friction during the setting process, it reduces the local heat development during the setting process, and it thus reduces the wear and tear risk to the expanding ring (28) and in particular reduces the wear and tear on the expanding packer end element (16).
In an embodiment of the invention the casing packer with slips is arranged for withstanding a pull in its set state of 136.2 tons pull. In an embodiment of the invention the casing packer seal arrangement (100) is arranged for the force pulled on the slidable inner sleeve is 30 ton or 30000 kgf, or 294000 N, but our present experience is that the expanding ring (28) and the packer end element (16) for a 95/8'' casing packer is fully expanded and set in the surrounding casing already at about 3.5 tons pulling force, corresponding to 3500 kgf or 34300 N, and for the third embodiment run on a 13 5/8 '' casing packer is fully expanded at about 3.9 tons, corresponding to 3900 kgf or 38250 N.
An advantage of this is that the casing packer assembly of the present invention is easily set, it may endure a high setting force but will expand and seal early. A further advantage is that when "crossing" over to an opposite annular pressure, e.g. from a pressure from below such as in Fig.1a, to a pressure from above such as in the same figure, the axial force on the packer seal may shift, but the axial force required to maintain the expanding ring (28) in the set state is comparably rather low, so the ratchet-set force of 30 tons is sufficient to maintain the complete sealing effect.
In an embodiment of the invention, the first embodiment of expanding ring (28) illustrated in Fig.7a, Fig.7b, Fig.8, and Fig.8a, said slit path (28s) comprises a transition from said planar slit portion (28sp) to a low-angle helical slit portion (28a) further towards said opposite rear face (28r) of said expanding ring (28). In this embodiment said expanding ring (28) being made of one single material part. The end of the helical slit portion may be cut-off straight in order to avoid deformation of the final sharp end, please see Fig.7a.
In an embodiment of the invention, the second embodiment of expanding ring (28), said slit path (28s) comprises a transition from said planar slit portion (28sp) to a generally transverse cut highangle slit portion (28c), please see Fig.8b, Fig.9a, and in particular Fig.9b, and further in Fig.9c, said high-angle slit portion (28c) continuing towards said opposite rear face (28r) of said expanding ring (28).
In a further embodiment to the above second embodiment of the expanding ring (28) shown in Fig. 8b, Fig.9a, and in particular Fig.9b, and further in Fig.9c, there is a circumferential peripheral groove (28gr) with plane walls, arranged circumferentially in said expanding ring, wherein
- said peripheral, circumferential groove (28gr) housing first and second internal expanding rings (28ai ,28bi),
- said expanding rings (28ai ,28bi) having a slot, and
- said expanding rings (28ai, 28bi) having their slot at mutually different peripheral angles and also with regard to a peripheral position of said notch (28n) and said planar slit portion (28sp).
In this embodiment, the continuous, un-slotted parts of the inner expanding rings (28ai, 28bi) (which is every part except for near the slots) has good mechanical bending moment resistance in the axialorthogonal plane, so as for lying as a double ring layer (28ai, 28bi) for supporting the arc-shaped gap revealing behind the tongue (28x). This prevents buckling-in of the expanding ring (28) in general when subject to high axial load and local pressure-induced loads from the packer end element (16), thus reducing the risk of undesired extrusion of packer end element (16).
One advantage of this embodiment is that the combined expanding resistance stiffness, or the "peripheral expanding or "widening" bending moment resistance" of the expanding ring (28), the U-shaped bottom ring and including the first and second internal expanding rings (28ai, 28bi), is reduced, both separately and combined as compared to a expanding ring which is through solid in its entire cross-section. Thus, it is reasonable to assume that the expanding ring (28, 28ai, 28bi) is more flexible to adapt to and thus follow the actual inner surface shape of the surrounding casing pipe wherein the packer shall be set. In the embodiment shown in Figs.8b, 9a, and 9c, each internal expanding ring (28ai, 28bi) cross-section has a Gamma-like shape (Γ) with a wider radially outer portion and a narrower stem portion.
In an embodiment of the invention the first internal expanding ring (28ai) has an outer plane circular surface (28aib) which is forming part of said shallow, planar, peripherally widening arc-shaped recess bottom (28B) that is uncovered between the peripherally widening notch gap's (28n) opposite faces, said planar slit portion (28sp) underlying said arc-shaped tongue (28te) of even thickness along the entire length of said planar slit portion (28sp).
In an embodiment of the invention there is arranged radial expansion slits (28x) , please see Fig.7b, Fig.9b, Fig.9c, said slits (28x) cut in from a radially inner face of said expanding ring (28), said expansion slits (28x) for reducing widening bending moment resistance stiffness of said expanding ring, thus reducing the required axial force for fully expanding the expanding ring (28).
One further advantage of this expansion-slitted (28x) embodiment, combined with the above generally transverse cut high-angle slit portion (28c) towards said opposite rear face (28r) of said expanding ring (28), is that the peripheral length of the total slit (28s) becomes relatively short, and the remaining length available for distributing the slits (28x) becomes correspondingly long, so as for allowing many of those radial slits (28x) distributed radially internally along the inner periphery of the "intact" expanding ring (28), thus allowing a better distributed, more even peripheral bending moment resistance around the expanding ring, thus better enabled to adapt to a non-perfect inner wall of a casing pipe to be sealed, without compromising on the axial loading properties of the expanding ring (28).
In an embodiment of the invention, please see Fig.9c, lower part, said internal expanding rings (28ai, 28bi) are mutually fixed by an axial-parallel fixing screw (28f) across said circumferential groove (28gr) in one common position on said expanding ring (28), said common position peripherally at least 30 degrees away from said gaps of said internal expanding rings (28ai, 28bi) and said notch gap (28n).
In an embodiment of the invention such as shown in Fig.9b and in Fig.9c, middle part, the peripheral, circumferential groove (28gr) profile has a base shoulder portion (28bs) which extends behind said planar slit (28sp), so as for, together with said expanding inner ring (28ai), supporting said arc-shaped tongue (28te) for facing said packer end element (16). An advantage of this embodiment is that when the arc-shaped gap formed as the tongue (28te) slides open, the radially lower portion of the tongue (28te) always has a mechanical backing from this base shoulder portion (28bs). When the ring (28) expands, the radially packer-facing face of the base shoulder portion (28bs) forms part of the shallow arc-shaped recess which mechanically supports the outer plane ring portion (16o) of the expanding packer.
In an embodiment of the invention, there is a third embodiment of the expanding ring (28), wherein said expanding ring (28) comprises:
- a slotted base expanding ring (28Y) connected to an internally conic, expanding disc ring stack (28d3, 28d2, 28d1), please see Fig.8c, Fig.11, and Fig.12. The expanding disc stack (28d3, 28d2, 28d1) comprising
- a third, slotted (28g3), internal-conically bevelled expanding disc ring (28d3),
- a second, slotted (28g2), internal-conically bevelled expanding disc ring (28d2),
- a first, slotted (28g1, 28n), internal-conically bevelled expanding disc ring (28d1) wherein said first slot forms said first slit gap (28n);
said slotted base expanding ring (28Y) and expanding disc ring stack (28d3, 28d2, 29d1) connected by an assembly screw connection (28Ys) at a peripheral position away from said first slot (28g1, 28n). The first slotted expanding disc ring (28d1) is the one which forms the ring-shaped outer face (28o) which encounters the radially plane outer ring portion (16o) of the expanding packer end element (16).
In an embodiment of the invention, the peripheral angles between gaps formed by said slots (28g1, 28g2, 28g3) forming part of the slit path (28s) through the expanding ring (28) are distributed as follows in the table, with reference to the upper left portion of Fig.11:
With these peripheral angles, there will be an extensive peripheral length of arc support behind the notch (28n) formed by the first gap (28g1). Behind this first gap (28g1) there will be a double layer of expanding disc ring (28d2 and 28d3) supporting 75 degrees behind, and 90 degrees ahead, along and behind supporting the outer arch-shaped plane face (28o).
Further, the base expanding ring behind these two expanding disc rings (28d2, 28d3) will have continuous mechanical support 45 degrees behind and "endless" ahead of the base expanding ring (28be). This increases the mechanical strength of the support under the arc-shaped plane face (28o) and the recession bottom (28b) formed by the expanding arc-shaped ap (28g), thus buckling of the expanding ring (28) is prevented, and further yield of the packer end element (16) further than the thickness of expanding disc ring (28d1) is prevented.
Thus, in this third embodiment of the expanding ring (28), the slit path (28s) runs as follows:
The invention comprises a casing packer section for being inserted together with a liner, patch or casing in a casing in a well, the casing packer section comprising a casing packer seal arrangement of the above.
The invention also comprises a bridge plug or retrievable bridge plug with a casing packer seal arrangement according to the above description.
Claims (22)
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| NO20220791A NO20220791A1 (en) | 2022-07-11 | 2022-07-11 | Mechanical Casing Annulus Packer II |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| NO20220791A NO20220791A1 (en) | 2022-07-11 | 2022-07-11 | Mechanical Casing Annulus Packer II |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| NO20220791A1 true NO20220791A1 (en) | 2020-05-25 |
Family
ID=83586993
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| NO20220791A NO20220791A1 (en) | 2022-07-11 | 2022-07-11 | Mechanical Casing Annulus Packer II |
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| Country | Link |
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| NO (1) | NO20220791A1 (en) |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CA1280362C (en) * | 1987-04-13 | 1991-02-19 | Thomas F. Bailey | Whipstock packer assembly |
| US20020043368A1 (en) * | 2000-10-12 | 2002-04-18 | Greene, Tweed Of Delaware, Inc. | Anti-extrusion device for downhole applications |
| US9784066B1 (en) * | 2015-07-09 | 2017-10-10 | Christopher A. Branton | Downhole bridge plug or packer assemblies |
| US20170350211A1 (en) * | 2016-06-02 | 2017-12-07 | Weatherford Technology Holdings, Llc | Anti-extrusion barrier for packing element |
| US20180023366A1 (en) * | 2016-01-06 | 2018-01-25 | Baker Hughes, A Ge Company, Llc | Slotted Backup Ring Assembly |
| WO2018056951A1 (en) * | 2016-09-20 | 2018-03-29 | Halliburton Energy Services, Inc. | High expansion metal back-up ring for packers and bridge plugs |
-
2022
- 2022-07-11 NO NO20220791A patent/NO20220791A1/en unknown
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CA1280362C (en) * | 1987-04-13 | 1991-02-19 | Thomas F. Bailey | Whipstock packer assembly |
| US20020043368A1 (en) * | 2000-10-12 | 2002-04-18 | Greene, Tweed Of Delaware, Inc. | Anti-extrusion device for downhole applications |
| US9784066B1 (en) * | 2015-07-09 | 2017-10-10 | Christopher A. Branton | Downhole bridge plug or packer assemblies |
| US20180023366A1 (en) * | 2016-01-06 | 2018-01-25 | Baker Hughes, A Ge Company, Llc | Slotted Backup Ring Assembly |
| US20170350211A1 (en) * | 2016-06-02 | 2017-12-07 | Weatherford Technology Holdings, Llc | Anti-extrusion barrier for packing element |
| WO2018056951A1 (en) * | 2016-09-20 | 2018-03-29 | Halliburton Energy Services, Inc. | High expansion metal back-up ring for packers and bridge plugs |
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