CN106481306B

CN106481306B - Rubber sleeve with lower end sealing ring inner side surface not coated with copper sheet, packer and bridge plug

Info

Publication number: CN106481306B
Application number: CN201611129679.XA
Authority: CN
Inventors: 宋炜; 隆学武
Original assignee: Tianding Sealing Technology (beijing)co Ltd
Current assignee: Tianding Sealing Technology (beijing)co Ltd
Priority date: 2016-07-06
Filing date: 2016-12-09
Publication date: 2023-03-28
Anticipated expiration: 2036-12-09
Also published as: CN106481306A; CN106014329A

Abstract

The application relates to the field of sealing, in particular to a rubber sleeve, a packer and a bridge plug which are used in the petroleum exploitation industry and can bear high temperature and high pressure and the inner side surface of a lower end sealing ring is not coated with copper sheets. The lower end sealing ring of the rubber cylinder is coated with a first copper sheet, and the first copper sheet coats the upper surface, the lower surface and the outer side surface of the lower end sealing ring but does not coat the inner side surface of the lower end sealing ring; the thickness of first copper sheet sets up to, works as the upper end bears during first axial pressure, the lower extreme sealing ring is in radial direction takes place deformation and makes distribution in the lower extreme sealing ring first copper sheet on the medial surface can conflict with the center tube to and distribute in the lower extreme sealing ring first copper sheet on the surface can conflict with the sleeve pipe. The lower extreme sealing ring cladding of this application has first copper sheet, reduces or has prevented the degradation effect of the micro molecule of high temperature high pressure steam to the packing element, has improved the sealed long-term of packing element.

Description

Rubber sleeve with lower end sealing ring inner side surface not coated with copper sheet, packer and bridge plug

Technical Field

The application relates to the field of sealing, in particular to a rubber sleeve, a packer and a bridge plug which are used in the petroleum exploitation industry and can bear high temperature and high pressure and the inner side surface of a lower end sealing ring is not coated with copper sheets.

Background

The packer is a key tool for oil extraction in the oil field, is widely applied to multiple operations such as oil field separate injection, layered reconstruction, layered oil extraction, mechanical pipeline water plugging and the like, needs to perform annular packing to realize oil gas layering, and the core component for realizing annular packing is a rubber sleeve. Bridge plugs are also a commonly used tool for oil and gas stratification in oil production operations. The main difference between packers and bridge plugs is that packers are typically temporarily left in the well during fracturing, acidizing, leak finding, etc., while bridge plugs are temporarily or permanently left in the well during seal production, etc. The packer and the central pipe are left in the well at the same time, the well can be left alone by setting up the releasing tool, and the well can be left alone by the bridge plug. Structurally, the packer is a hollow structure and can freely flow oil, gas and water, and the bridge plug is a solid structure.

As the tool of oil-gas separation, the packer and the bridge plug all need the packing element, and the packing element is as sealed key component, and its quality directly influences the sealed effect and the life of packer and bridge plug, plays decisive effect in packer and bridge plug. The rubber tube is generally made of rubber materials, so the rubber tube is called as a rubber tube. The rubber tube is a popular technical term in the industry, and is used for indicating functional components for sealing, and not only means that the rubber tube can be made of rubber. When the rubber cylinder bears a certain pressure to cause the rubber cylinder to deform for sealing, the deformation capacity of the rubber cylinder needs to be considered, and if the deformation is insufficient, the rubber cylinder cannot play a sealing role; if the deformation is too large, the rubber cylinder may fail due to crushing and lose the recovery capability. Most importantly, when the rubber cylinder is acted by high-temperature steam in the well, the rubber cylinder is acted by high temperature and high pressure to fail and lose the recovery capability.

Ninth-phase petroleum machinery in 2002 discloses a new structure of a packer compression rubber cylinder for preventing outburst, wherein the new structure is described as follows: "outburst prevention" means that some kind of stop ring, support, restriction device, protector, etc. is placed at the end of the rubber sleeve to organize and restrict the rubber sleeve from protruding or flowing towards the oil jacket annular space when the packer is set. The protruding-proof structure is used for covering the annular gap between the packer and the casing, when the packer is set, once the rubber cylinder deforms and contacts with the casing wall, under the action of external load, the protruding-proof device can be unfolded to cover the annular gap between the packer and the casing wall, the rubber cylinder is prevented from protruding towards the annular gap, the rubber cylinder is forced to be in a uniform compression state in all directions, and high contact stress of the rubber cylinder is generated and maintained, so that good sealing is obtained. "\8230" \\8230, mainly includes two types, copper bowl curing type and steel net or steel belt curing type. The former is to solidify two copper bowls with the thickness of 2mm on one end surface of the two end rubber cylinders respectively, and the latter is to solidify a steel mesh or a steel belt with the thickness of about 1mm on one end surface of the two end rubber cylinders respectively.

The first petroleum mine machinery of 2013 discloses an article of packer rubber cylinder structure improvement and advantage analysis, wherein the following contents are described: "3 packing elements are strung on the packer commonly used, divide into upper, middle, 3 packing elements structure sizes the same and upper and lower packing elements are long packing elements, middle packing element is 2 structural style of short packing element. Through research on the traditional three-rubber-cylinder structure, the upper rubber cylinder plays a main sealing role. And, nonlinear analysis is performed by nonlinear finite element analysis software Abaqus to obtain: the axial compression amount is increased along with the increase of the axial load, the compression amount is obviously increased at the beginning, and then the compression amount is increased and slowed down, so that the deformation of the rubber cylinder tends to be stable; along with the increase of the setting force, the contact length of the rubber sleeve and the sleeve gradually increases. The radial deformation of the cylindrical surface part of the outer surface of the rubber cylinder is limited, the deformation of the inner surface of the rubber cylinder is outwards bulged like the appearance, and the rubber cylinder is flattened and compacted at last when the load is increased. However, due to structural constraints, only the sizing cylinder can be compacted. When the working pressure is 30MPa, the upper rubber cylinder is basically and completely compacted, the upper end of the rubber cylinder has slight shoulder projection, but the rubber cylinder is not cut, and the shoulder projection is within an allowable range.

In the "improvement of a high-pressure packer sealing rubber cylinder" in the first phase of 2009, petroleum mine machinery ", it is considered that" a metal sheet (e.g., a copper sheet) is added to the rubber surface layer because the rubber surface layer is easily torn ".

The above prior art only analyzes the effect of applying a first axial pressure (equivalent to an "axial load") on the deformation of the cartridge. In the actual production process, however, a first axial pressure from top to bottom needs to be applied to the rubber cylinder to seal the rubber cylinder; then a second axial pressure (the impact of substances such as gas at the bottom of the well and the like on the rubber cylinder) from bottom to top is applied to the rubber cylinder. According to the inventor's experiment, when the first axial pressure is 30MPa, the inventor found that almost all of the rubber cylinders have shoulder protrusions, and when the second axial pressure (for example, 15 Ma) is further applied, all of the rubber cylinders have cracks at the shoulder protrusions, so that the sealing is failed.

Further, the inventor also finds that even if the rubber sleeve can be sealed, when substances such as bottom hole gas and the like impact the rubber sleeve, small molecules of high-temperature and high-pressure steam contained in the rubber sleeve can degrade the rubber sleeve made of high polymer materials, so that the rubber sleeve loses elasticity at the lower end part and cannot play a sealing role, and the long-term effect of sealing the rubber sleeve is influenced.

Disclosure of Invention

It is an object of the present application to provide a new structural design of the cartridge to prevent cartridge seal failure.

According to one aspect of the present application, there is provided a rubber cylinder having a through hole at a center, an inner surface at the through hole, an outer surface corresponding to the inner surface, an upper end portion and a lower end portion at both ends of the rubber cylinder, respectively, the upper end portion being adapted to receive a first axial pressure in an axial direction, and the lower end portion being adapted to receive a second axial pressure in the axial direction opposite to the first axial pressure; when the first axial pressure is applied to the upper end part, the middle part and the lower end part are deformed in the radial direction; when the second axial pressure is applied to the lower end part, the upper end part, the middle part and the lower end part are deformed in the radial direction, the rubber cylinder is formed by arranging an upper end sealing ring at the upper end, a lower end sealing ring at the lower end and more than one middle sealing ring between the upper end sealing ring and the lower end sealing ring in the axial direction, the upper end sealing ring serves as the upper end part, the lower end sealing ring serves as the lower end part, and the middle sealing ring serves as the middle part;

the lower end sealing ring is coated with a first copper sheet, and the upper surface, the lower surface and the outer side surface of the lower end sealing ring are coated with the first copper sheet but not coated with the inner side surface of the lower end sealing ring; the thickness of first copper sheet sets up to, works as the upper end bears during first axial pressure, the lower extreme sealing ring is in radial direction takes place deformation and makes distribution in the lower extreme sealing ring first copper sheet on the medial surface can conflict with the center tube, and distribution in the lower extreme sealing ring first copper sheet on the surface can conflict with the sleeve pipe.

Preferably, the opening edge of the first copper sheet is flush with the inner side surface of the lower end sealing ring.

Preferably, a third copper sheet is coated outside the upper end sealing ring, and the third copper sheet coats the upper surface, the lower surface and the outer side surface of the upper end sealing ring but does not coat the inner side surface of the upper end sealing ring; the third copper sheet is thick enough so that, when the lower end receives the second axial pressure, the third copper sheet covering the shoulder formed by the upper surface of the upper end seal ring does not break.

Preferably, the number of the middle sealing rings is three, wherein the middle sealing ring at the lowermost end and the middle sealing ring at the uppermost end are both coated with copper sheets, and the middle sealing ring is not coated with copper sheets.

Preferably, the hardness of the upper end seal ring is greater than the hardness of the middle seal ring, so that the deformation of the middle seal ring in the radial direction is greater than the deformation of the upper end seal ring in the radial direction when the upper end seal ring is subjected to the first axial pressure;

the hardness of the lower end sealing ring is greater than the hardness of the middle sealing ring, so that when the lower end sealing ring bears the second axial pressure, the deformation of the middle sealing ring in the radial direction is greater than the deformation of the lower end sealing ring in the radial direction.

Preferably, the hardness of the upper end sealing ring is substantially the same as that of the lower end sealing ring, so that when the upper end sealing ring is subjected to the first axial pressure, the deformation of the middle sealing ring in the radial direction is greater than the deformation of the upper end sealing ring and the lower end sealing ring in the radial direction, and when the lower end sealing ring is subjected to the second axial pressure, the deformation of the middle sealing ring in the radial direction is greater than the deformation of the upper end sealing ring and the lower end sealing ring in the radial direction.

Preferably, the intermediate sealing ring has a colloid and a ring-shaped substrate, the substrate is composed of a plurality of mutually crossed high-temperature and high-pressure resistant fiber filaments, the colloid is bonded to each of the fiber filaments, and the colloid is distributed on the surface of each of the substrates so that the inner surface and the outer surface are respectively formed by the inner part and the outer part of the plurality of sealing rings arranged along the axial direction.

Preferably, the substrate is a graphite packing or a carbon fiber packing or a glass fiber packing.

According to another aspect of the present application, a packer is provided having a packing element as defined in one of the above-mentioned aspects.

According to a further aspect of the present application, there is provided a bridge plug having a cartridge as defined in one of the above aspects.

The technical scheme provided by the application at least has the following technical effects:

1. according to the technical scheme of the application, the hardness of the upper end part is larger than that of the middle part, so that when the upper end part is subjected to the first axial pressure, the upper end part transmits the first axial pressure to the middle part and the lower end part rather than being used for radial deformation of the upper end part. Thus, the middle part and the lower end part can be radially deformed when a small first axial pressure is used, and the whole rubber cylinder is sealed.

2. According to the technical scheme of the application, under the condition that the hardness of the middle part is unchanged, the hardness of the upper end part is set to be larger than that of the middle part, so that when the first axial pressure with the same magnitude acts on the upper end part, the deformation of the upper end part in the radial direction is smaller, and particularly, the shoulder protrusions formed by the radial deformation of the upper end part are smaller correspondingly. The smaller shoulder can effectively prevent the rubber cylinder from being cut apart, and the effect of preventing the rubber cylinder from sealing failure is achieved.

3. In one embodiment, as the base body comprises the plurality of fiber yarns, the sealing rings are harder when the number of the fiber yarns is larger, and the sealing rings are softer when the number of the fiber yarns is smaller, so that the hardness degree of the sealing rings can be adjusted according to the number of the fiber yarns, the hardness of the whole rubber cylinder can be directly changed by changing the hardness of the sealing rings, and the purpose of increasing the compression strength range of the rubber cylinder is achieved.

4. The matrix of this application has the cellosilk of intercrossing, and the colloid bonds each cellosilk. When the rubber cylinder expands under the first axial pressure, the fiber filaments limit the expansion, so that the structural rigidity of the rubber cylinder is integrally increased, and the compressive strength of the rubber cylinder is increased.

5. A plurality of sealing ring axial arrangement that this application relates to if there is individual sealing ring to damage in the oil development in-process, can change the sealing ring of damage for new sealing ring, and all the other sealing rings no longer change. Therefore, on the whole, the average service life of a single sealing ring is prolonged, the use amount of the rubber cylinder can be greatly reduced, and the production cost is reduced.

6. When the base member of this application selects for the packing, can choose present high temperature resistant highly compressed packing for use, like this, combine with graphite packing or carbon fiber packing and when becoming the sealing ring when the colloid, the packing wholly can play the supporting role, and the colloid can play the effect of deformation and sealed enhancement. Present packing is selected for use to this application, and need not make the special packing that is used as the base member, can increase the flexibility of production. According to the knowledge of the inventor, the existing graphite packing and carbon fiber packing can resist the action of high temperature and high pressure, but the resilience of the graphite packing and the carbon fiber packing is poor. In this application, the colloid dispersion is among the packing, and the packing that helps the compressed packing to kick-back after first axial pressure disappears to be favorable to the packing element to take out from the pit.

7. The base member of this application all becomes the contained angle with the radial direction of packing element, receives first axial pressure effect when the packing element like this, and the sealing ring at first becomes parallel with the radial direction of packing element, and then the sealing ring just carries out radial inside and outside arch. And in the state that the sealing ring is changed from the inclined state to be parallel to the radial direction, the sealing ring does not generate the deformation in the radial direction, and only the rubber cylinder generates the deformation in the radial direction. Therefore, the deformation of the rubber cylinder in the radial direction is increased, and the defects that the rubber cylinder is hard and the deformation in the radial direction is insufficient can be overcome.

8. The utility model provides a lower extreme sealing ring cladding has first copper sheet, reduces or has prevented the micromolecule of high temperature high pressure steam to the degradation of packing element, has improved the long-term nature that the packing element is sealed.

Drawings

Some specific embodiments of the present application will be described in detail hereinafter by way of example and not by way of limitation with reference to the accompanying drawings. The same reference numbers in the drawings identify the same or similar elements or components. In the drawings:

FIG. 1 is a schematic illustration of a compression packer including a packer with a base pipe and casing according to an embodiment of the present application;

FIG. 2 is a schematic illustration of the positional relationship of the glue cartridge to the center tube and the sleeve according to one embodiment of the present application, wherein only a portion of the glue cartridge, the center tube and the sleeve are shown;

FIG. 3 is a schematic diagram showing the shoulder of the cartridge of FIG. 2 in a first axial pressure application relationship with the center tube and the sleeve, but without a second axial pressure application;

FIG. 4 is a schematic diagram of the construction of a glue cartridge according to one embodiment of the present application;

FIG. 5 is a schematic structural view of a seal ring according to an embodiment of the present application;

FIG. 6 is a cross-sectional schematic view of a seal ring according to an embodiment of the present application;

FIG. 7 is a cross-sectional schematic view of a seal ring according to an embodiment of the present application;

FIG. 8 is a cross-sectional schematic view of a seal ring according to an embodiment of the present application;

FIG. 9 is a cross-sectional schematic view of a seal ring according to an embodiment of the present application;

FIG. 10 is a cross-sectional schematic view of a seal ring according to an embodiment of the present application;

FIG. 11 is a schematic view of another embodiment of the cartridge of the present application;

FIG. 12 is a schematic view of a construction of a cartridge according to yet another embodiment of the present application;

FIG. 13 is a schematic view of the cartridge of FIG. 12 after compression by a first axial compressive force;

FIG. 14 is a schematic structural view of a constraining sheath according to an embodiment of the present application;

FIG. 15 is a schematic structural view of a cartridge containing a constraining sheath according to one embodiment of the present application, showing the constraining sheath in positional relationship with the rest of the cartridge before compression;

FIG. 16 is a schematic view of the cartridge of FIG. 15 during compression by a first axial compressive force;

FIG. 17 is a schematic view of the cartridge of FIG. 15 after compression by a first axial compressive force, showing the positional relationship of the constraining sheath to the remainder of the cartridge after compression;

FIG. 18 is a schematic diagram of a three-segment glue cartridge according to one embodiment of the present application.

The reference numbers in the figures are as follows:

10-rubber cylinder, 101-outer surface, 102-inner surface, 103-through hole, 104-upper end part, 105-middle part, 106-lower end part, 107-shoulder;

108-substrate, 109-colloid, 111-first copper sheet, 111 a-inner copper sheet, 111 b-outer copper sheet, 111 c-opening, 111 d-upper copper sheet, 111 e-lower copper sheet, 112-second copper sheet, 113-third copper sheet;

20-a restraining sleeve, 21-a necking end and 22-a flaring end;

30-a central tube;

40-a cannula;

50-rigid spacer ring;

60-bulge;

70-sealing ring, 71-upper end sealing ring, 72-middle sealing ring, 73-lower end sealing ring;

200-compression packers;

a-a first axial direction;

b-a second axial direction;

F ₁ -a first axial pressure;

F ₂ -a second axial pressure.

Detailed Description

The directions "up" and "down" described below are described with reference to fig. 2.

The compression packer 200 shown in FIG. 1 has a packing element 10 of the present application. A compression packer 200 is attached to the base pipe 30 and placed within the casing 40. The compression packer 200 is required to separate different oil layers and water layers in a shaft and bear a certain pressure difference, and is required to be capable of being lowered to a preset position of the shaft to be tightly sealed, and also to have durability in the shaft and be capable of being smoothly lifted out when needed.

As shown in FIG. 2, the rubber cylinder 10 is arranged between the sleeve 40 and the central tube 30Within the annular space, the rigid spacer ring 50 provides a first axial compressive force F in the axial direction from top to bottom (i.e., the first axial direction A) ₁ In other embodiments, rigid spacer ring 50 may be eliminated and first axial compressive force F applied to cartridge 10 ₁ Other components of (a). As shown in fig. 2, the rubber tube 10 has an upper end 104 and a lower end 106 at both ends, and an intermediate portion 105 located between the upper end 104 and the lower end 106. The upper end portion 104 is used for bearing a first axial pressure force F along the axial direction ₁ The lower end 106 is adapted to receive a first axial pressure force F in the axial direction ₁ Opposite second axial pressure force F ₂ . The upper end portion 104, the lower end portion 106 and the middle portion 105 should be resilient as part of the cartridge 10. As an explanation for the elasticity and limitation of the magnitude of the elasticity, when the first axial pressure F is applied ₁ When applied to the upper end portion 104, the intermediate portion 105, and the lower end portion 106 are deformed in the radial direction; when the second axial pressure F ₂ When applied to the lower end 106, the upper end 104, the intermediate portion 105, and the lower end 106 are all deformed in the radial direction. In the embodiment shown in fig. 2, both the upper end 104 and the lower end 106 have beveled edges, which may not be provided in other embodiments.

As shown in FIG. 3, the inventors have discovered that when the upper end portion 104 is subjected to a first axial compressive force F ₁ When the second axial pressure F is applied, the upper end portion 104 generates a large shoulder 107 ₂ The upper end 104 may rupture at the shoulder 107 in fig. 3.

The structural design of the present application to reduce or prevent shoulder 107 is described below.

In the embodiment shown in fig. 4, the rubber tube 10 is cylindrical as a whole, and the rubber tube 10 has a through hole 103 at the center, the through hole 103 being defined by an inner surface 102, and an outer surface 101 being located at the outer side of the through hole 103 corresponding to the inner surface 102. When the first axial pressure F ₁ Acting in a first axial direction A on the upper end 104 or on a second axial pressure F ₂ When acting on the lower end 106 in the second axial direction B, the rubber sleeve 10 as a whole will be compressed axially and expanded radially (in the same sense as "deformation in radial direction") to urge the outer surface 101 to bulge outwardsThe inner surface 102 is convex inward, but the outer surface 101 is generally convex partially outward in time sequence. Under the application of a first axial pressure F ₁ Thereafter, the inner surface 102 seals with the center tube 30 of FIGS. 1 and 2 and the outer surface 101 seals with the sleeve 40 of FIGS. 1 and 2. Generally, the inner surface 102 is less open to the center tube 30 (nearly flush) and the outer surface 101 is more open to the jacket 40, resulting in the outer surface 101 being outwardly convex than the inner surface 102 being inwardly convex, since the center tube 30 and jacket 40 define the maximum convex size of the inner surface 102 and outer surface 101, respectively.

As mentioned above, the upper end portion 104, the lower end portion 106 and the intermediate portion 105 should all be resilient, but in the embodiment shown in fig. 2 and 4 the upper end portion 104 has a hardness greater than the intermediate portion 105. The upper end portion 104 is subjected to a first axial compressive force F ₁ At this time, the deformation of the middle portion 105 in the radial direction is larger than the deformation of the upper end portion 104 in the radial direction.

Since the upper end portion 104 has a hardness greater than that of the intermediate portion 105, the upper end portion 104 is subjected to a first axial compressive force F ₁ The upper end 104 more than applies the first axial pressure force F ₁ To the intermediate portion 105 and the lower end portion 106 rather than for radial deformation thereof. This enables the use of a smaller first axial pressure force F ₁ The intermediate portion 105 and the lower end portion 106 are radially deformed, and the rubber tube 10 is sealed as a whole. The inventors have found in tests that if the hardness of the upper end portion 104 is not greater than the hardness of the intermediate portion 105, the upper end portion 104 is subjected to the first axial compressive force F ₁ More so than for its radial deformation, instead of being transmitted to the intermediate portion 105 and the lower end portion 106, preventing or reducing the shoulder 107 as shown in fig. 3.

According to the solution of the present application, the hardness of the upper end portion 104 is set to be greater than the hardness of the middle portion 105 without changing the hardness of the middle portion 105, so that the same magnitude of the first axial compressive force F is applied to the upper end portion ₁ In this case, the upper end portion 104 is deformed less in the radial direction, and it is particularly noted that the shoulder 107 formed by the radial deformation of the upper end portion 104 is also smaller. Compared withThe small shoulder 107 can effectively prevent the rubber sleeve 10 from being cut, and the effect of preventing the sealing failure of the rubber sleeve 10 is achieved.

Since the radial deformation of the upper end portion 104 is relatively small, it is likely that the deformation of the upper end portion 104 in the radial direction will be insufficient to seal the sleeve 40 with the central tube 30, i.e. the upper end portion 104 will no longer function as a seal but will only be subjected to the first axial pressure force F ₁ To the intermediate portion 105 and the lower end portion 106, which is an important difference of the glue cartridge 10 of the present application from the glue cartridges of the prior art. Moreover, even if the radial deformation of the upper end portion 104 is large to seal the sleeve 40 and the center tube 30, the sealing of the upper end portion 104 is only a supplement to the sealing of the rubber tube 10, and the hardness of the upper end portion 104 is set to be greater than the hardness of the middle portion 105 regardless of whether the upper end portion 104 performs a sealing function, so that the rubber tube 10 is prevented from being cut due to the excessive shoulder 107, and the first axial pressure F can be made small ₁ The cartridge 10 is sealed.

According to the solution of the present application, the hardness of the upper end portion 104 is set to be greater than the hardness of the intermediate portion 105 without changing the hardness of the intermediate portion 105, but the upper end portion 104 is pressed in the first axial direction F by the upper end portion 104 in this way ₁ And may not be in contact with the sleeve 40 and may not act as a seal. With this particular construction, when the lower end portion 106 and the intermediate portion 105 are substantially the same hardness, the sealing of the cartridge of the present application is provided by the lower end portion 106 and the intermediate portion 105; the sealing of the glue cartridge of the present application is provided by the intermediate portion 105, when the lower end portion 106 is substantially the same hardness as the upper end portion 104. The cartridge 10 of this sample application is completely different from the prior art cartridges in the structure for sealing.

As a preferred embodiment, when the outer wall of the upper end portion 104 abuts against the inner wall of the sleeve 40, and more preferably, when the outer wall of the upper end portion 104 is sealed against the inner wall of the sleeve 40, the lower portion of the upper end portion 104 covers the upper portion of the middle portion 105 with substantially equal area, and there is substantially no difference in radial direction between the upper end portion 104 and the middle portion 105, so as to generate downward pressing effect on the joint of the middle portion 105 and the upper end portion 104, and prevent or reduce the occurrence of shoulder protrusion at the joint of the middle portion 105 and the upper end portion 104.

If the first axial pressure F is to be increased in order to achieve the above-mentioned "more ₁ The effect of transmitting the force to the intermediate portion 105 and the lower end portion 106, not for the radial deformation itself "and the effect of the shoulder 107 not being produced by the upper end portion 104, a metal block that is not easily deformed, such as an iron block, may be used. If the diameter of the metal block is small, the intermediate portion 105 in contact with the metal block generates a larger shoulder 107, and if the diameter of the metal block is large, the metal block is not easily slid to an appropriate position in the sleeve 40 in consideration of the bending of the sleeve 40, and if foreign matter enters the sleeve 40, the large metal block is not easily pulled out from the sleeve. On the other hand, a smaller lifting force cannot pull the slug out of the casing 40, and a larger lifting force may damage the casing 40. In general terms, the upper end portion 104 used in the present application has elasticity, but the elasticity of the upper end portion 104 needs to be limited, i.e. the hardness of the upper end portion 104 is greater than that of the middle portion 105, so that the upper end portion 104 can be made smaller in diameter to facilitate movement within the casing, e.g. the upper end portion 104 can be the same diameter as the middle portion 105. Since the upper end portion 104 is hard, it is not easy to form the shoulder 107 itself or the formed shoulder 107 is small, and since the upper end portion 104 is deformed by being gradually extended in the radial direction at the time of compression, the gap between the upper end portion 104 and the sleeve 40 is reduced, thereby reducing or preventing the formation of the shoulder of the intermediate portion 105 and the size of the formation.

In one embodiment, the hardness of the lower end portion 106 is greater than the hardness of the intermediate portion 105 such that the lower end portion 106 is subjected to the second axial compressive force F ₂ In this case, the deformation of the intermediate portion 105 in the radial direction is larger than that of the lower end portion 106. Based on the same principle, such a structure can prevent the lower end portion 106 from being subjected to the first axial pressing force F ₁ Or the second axial pressure force F ₂ Shoulder is generated and the lower end portion 106 can be prevented from further receiving the second axial pressing force F in the case where the shoulder has been generated ₂ This causes the shoulder to become enlarged, thereby preventing the lower end 106 from being cut to cause the seal of the cartridge 10 to fail.

In another embodiment, the upper end 104 and the lower end 106 are substantially the same hardness, i.e., the hardness is substantially the sameIn other words, the upper end portion 104 and the lower end portion 106 have a hardness greater than that of the intermediate portion 105, so that they are subjected to the first axial pressing force F ₁ Or the second axial pressure force F ₂ At this time, the deformation of the middle portion 105 is larger than that of the upper end portion 104 and the lower end portion 106. This structure enables the intermediate portion 105 to quickly reach the sealed state, and prevents the shoulder portions of the upper and

lower end portions

104 and 106 from being generated or prevents the shoulder portions of the upper and

lower end portions

104 and 106 from being generated to be enlarged.

In the embodiment shown in fig. 2, 3 and 4, the cartridge 10 is comprised of three parts, an upper end 104, a lower end 106 and an intermediate part 105. Taking fig. 4 as an example, in the first axial direction a, that is, the top-to-bottom direction, the three seal rings 70 are an upper end seal ring 71, a middle seal ring 72 and a lower end seal ring 73, which are respectively located above and below. The upper end seal ring 71 serves as the upper end portion 104, the middle seal ring 72 serves as the middle portion 105, and the lower end seal ring 73 serves as the lower end portion 106. In the embodiment shown in fig. 11, the number of intermediate seal rings 72 located between the upper end seal ring 71 and the lower end seal ring 73 is three. In the embodiment shown in fig. 12 and 13, the number of intermediate seal rings 72 is nine. In other embodiments, the number of intermediate seal rings 72 may be provided in other numbers.

The shape and structure of the seal ring 70 will be described in detail below.

During the test, the inventor finds that the rubber tube 10 has a first axial pressure F required for setting due to the difference of hardness and softness of the rubber tube 10, for example, the rubber tube 10 made of polyetheretherketone is harder ₁ First axial pressure F of greater or nominal magnitude ₁ The lower rubber tube 10 is not deformed enough, so that the rubber tube 10 cannot play a sealing role. When the rubber tube 10 is made of soft rubber, the rubber tube 10 can not bear the first axial pressure F with the rated magnitude ₁ To be crushed or even be able to withstand the first axial pressure F ₁ But then subjected to a second axial pressure force F ₂ The rubber tube can also be crushed.

In the process of solving the problem of the softer rubber cylinder 10, the inventor dopes a plurality of mutually separated high-temperature and high-pressure resistant fiber filaments, such as graphite coil root filaments and glass fibers, in the rubber bodyAnd (5) keeping silk. Such a structure can solve the problem that the rubber tube 10 is soft as a whole to a certain extent. However, the inventors have further found that although the doped filaments are each connected to the glue, there is little or no connection between the individual filaments, so that the stiffness of the glue cartridge 10 can be increased only to a limited extent. Therefore, the inventor designs the following technical scheme: as shown in FIG. 5, the seal ring 70 is formed by forming a matrix 108 with a plurality of filaments intersecting with each other, and by distributing a gel 109 on the surface of the matrix 108 and bonding the filaments together, so that the seal ring 70 has ductility in the radial direction, or the seal ring 70 can be enlarged in diameter within a certain range without breaking (mainly breaking of the filaments) due to entanglement of the filaments, and during enlargement of the diameter of the seal ring 70, the intersecting filaments counteract a part of the first axial pressure F causing the diameter to be enlarged ₁ So that a larger first axial pressure force F is required to be provided if the diameter of the sealing ring 70 is to be increased to a certain extent ₁ . In particular, the glue 109 tightly bonds the intersecting filaments together, and a greater first axial pressure F is required to increase the diameter of the sealing ring 70 to a certain extent ₁ . In summary, the crossing of the filaments forms a resistance, and the glue 109 bonds the filaments together to form a resistance, under which the glue cartridge 10 is relatively hard to compress in its entirety, which is equivalent to the glue cartridge 10 becoming stiff in its entirety. When the number of filaments in a volume of the sealing ring 70 is substantially the same, the inventors have found that the number of filaments crossing each other can be adjusted by varying the thickness of the sealing ring, thereby adjusting the required first axial pressure F ₁ I.e., the amount of setting force applied to the cartridge 10. Likewise, the number of intersecting filaments, and thus the required first axial pressure F, may be adjusted by increasing the number of filaments within a volume of the sealing ring 70 ₁ Of (c) is used. The hardness of the upper end seal ring 71 made by the two methods can be made larger than that of the middle seal ring 72.

Returning to fig. 5, for the sake of structural clarity, fig. 5 only shows the gel 109 coated on all surfaces of the substrate 108, and does not show the gel 109 penetrating into the substrate 108. As an illustration of the surface here, the gel 109 in fig. 5 is located on the circumferential surface of the substrate 108, for example when the substrate 108 is circular in cross-section. In fig. 5, the substrate 108 is formed by polymerizing a plurality of high-temperature and high-pressure resistant filaments, for example, the filaments may be made of glass fibers or carbon fibers. In one embodiment, the individual filaments are woven together warp and weft to form the matrix 108, and in other embodiments the individual filaments may be woven together in other manners to form the matrix 108.

As can be seen from the above description, in the solution of the present application, it is not necessary that the fiber yarn has elasticity, since the shrinkage and expansion of the cartridge 10 are accomplished by the gel 109. As described above, the glue 109 is distributed on the surface and inside of each matrix 108 and bonds each filament. Ideally, the glue 109 bonds each filament and bonds the filaments together crosswise.

The copper coating on the cartridge 10 will be described in detail below.

The inventor found that if the rubber tube 10 is made of a suitable material after the problem of the shoulder 107 is solved, the rubber tube 10 can perform a sealing function, but the rubber tube 10 fails to seal even in a short time (for example, six hours) under a high-temperature and high-pressure environment, and the rubber tube 10 that has failed is found to fail not by the rupture of the shoulder 107 but by the collapse of the lower end portion 106 of the rubber tube 10. The fester is caused by the degradation of the rubber cylinder made of the high polymer material caused by the small molecules of high-temperature and high-pressure steam contained in the gas at the bottom of the well through research. When the rubber cylinder 10 is sealed, only the lower surface of the lower end portion 106 is in direct contact with the downhole gas, thereby causing the rubber cylinder 10 to degrade from bottom to top and fail.

In the embodiment shown in fig. 6, the sealing ring 70 is externally coated with a first copper sheet 111, and the first copper sheet 111 coats the lower surface (lower part), the inner side surface (left part), and the outer side surface (right part) of the sealing ring 70. It can be seen that the first copper sheet 111 has an opening 111c, and the opening 111c is located on the upper surface of the seal ring 70 and extends along the upper surface of the seal ring 70. In one embodiment, referring to FIG. 5, the opening 111c may also be constricted as an aperture along the upper surface of the seal ring 70. The opening 111c or the hole is designed to allow the gas remaining in the seal ring 70 to flow out when the seal ring provided at the upper portion presses the hole, and to prevent the high-temperature high-pressure gas from flowing into the hole. In the embodiment shown in FIG. 6, the opening 111c covers the second copper sheet 112, and in other embodiments, the opening 111c may be covered by the second copper sheet 112.

It should be considered that since the seal ring 70 is annular, the first copper sheet 111 covering the seal ring 70 is also annular, and the annular first copper sheet 111 is easily broken at the bent portion, in the embodiment shown in fig. 7, the first copper sheet 111 covers the upper surface, the lower surface, and the outer side surface of the seal ring 70, but does not cover the inner side surface (left portion) of the seal ring 70. Therefore, the first copper sheet 111 can be formed only by bending once, and the production efficiency of the first copper sheet 111 is improved. As mentioned above, the gap between the inner surface 102 and the central tube 30 is small (almost fit to each other) and the gap between the outer surface 101 and the sleeve 40 is large, so that the sealing ring 70 only needs a small inward protrusion to seal with the central tube 30 and a large outward protrusion to seal with the sleeve 40, and thus the surface not covered with the copper sheet is not selected on the outer side but on the inner side.

Referring to fig. 7, in fig. 7, the opening edge of the first copper sheet 111 is flush with the inner side surface of the sealing ring 70, and this design is to protect the upper and lower surfaces of the sealing ring 70 as much as possible without covering the inner side surface with the copper sheet, so as to reduce the degradation of the sealing ring 70 by the high-temperature and high-pressure steam.

In the embodiment shown in fig. 8, the sealing ring 70 is coated with a third copper sheet 113, the third copper sheet 113 covers the lower surface, the inner side surface, the outer side surface and the upper surface of the sealing ring 70, or the third copper sheet 113 covers the upper surface, the lower surface and the outer side surface of the sealing ring 70 but does not cover the inner side surface of the sealing ring 70. When the first copper sheet 111 further covers the upper surface of the lower end sealing ring 73, the shape of the first copper sheet is the same as that of the third copper sheet 113.

In the embodiment shown in fig. 9, the sealing ring 70 is covered by an inner copper sheet 111a and an outer copper sheet 111b, and the inner copper sheet 111a covers a part of the lower surface, the entire inner side surface (left portion) and a part of the upper surface of the sealing ring 70. The outer copper sheet 111b covers a part of the lower surface, the entire outer surface (right portion), and a part of the upper surface of the seal ring 70. And the inner copper sheet 111a and the outer copper sheet 111b have portions overlapping each other on both the upper surface and the lower surface.

In the embodiment shown in fig. 10, the sealing ring 70 is covered with an upper copper sheet 111d and a lower copper sheet 111e, and the upper copper sheet 111d covers a part of the inner side surface, the entire upper surface (upper side portion), and a part of the outer side surface of the sealing ring 70. The lower copper sheet 111e covers a part of the inner surface, the entire lower surface (lower portion), and a part of the outer surface of the seal ring 70. And the upper side copper sheet 111d and the lower side copper sheet 111e have parts overlapping each other on both the inner side surface and the outer side surface. In one embodiment, the upper copper skin 111d and the lower copper skin 111e are welded at an overlap to prevent direct contact of small molecules of high temperature, high pressure steam with the seal ring 70.

The embodiment shown in fig. 9 and 10 is also for reducing the number of the bent parts of the first copper sheet 111, preventing the first copper sheet 111 from being easily broken at the bent parts, and improving the production efficiency of the first copper sheet 111.

Referring to fig. 11, the cartridge 10 has an upper end seal ring 71, a lower end seal ring 73 and three intermediate seal rings 72. In this embodiment, the lower end seal ring 73 may be coated with a copper sheet having a structure as shown in fig. 6, 8 or 9. Thus, after the packing case 10 shown in fig. 11 is sealed, the lower surface of the lower end seal ring 73 can be prevented from being corroded and degraded by small molecules of high-temperature and high-pressure steam. Further, since the lower end sealing ring 73 only interferes with the central tube 30 and the sleeve 40 to perform only a slight sealing function, and there is a high possibility that a gap exists between the lower end sealing ring 73 and the sleeve 40, it is also necessary to cover the outer side surface of the lower end sealing ring 73 with a copper sheet. Because the upper surface of the lower end sealing ring 73 is pressed by the lower surface of the lowest end middle sealing ring 72, the direct contact with micromolecules of high-temperature high-pressure steam is isolated, and in this aspect, the upper surface of the lower end sealing ring 73 does not need to be covered with copper sheets. However, if the upper surface of the lower end sealing ring 73 is not covered with the copper sheet, the opening of the copper sheet is inevitably located on the outer side surface of the lower end sealing ring 73, and thus, in the process of radial deformation of the rubber cylinder 10 due to compression, the opening of the copper sheet may split the lower end sealing ring 73 itself or the lowermost intermediate sealing ring 72, and thus, in the embodiment shown in fig. 6, the opening 111c is located on the upper surface, and in order to further isolate direct contact with small molecules of high-temperature and high-pressure steam, the opening 111c covers the second copper sheet 112. In fig. 9, the inner copper sheet 111a and the outer copper sheet 111b are both U-shaped structures, and when the sealing ring is installed, the inner copper sheet 111a can be firstly sleeved on the sealing ring 70 from the inner side surface, and the outer copper sheet 111b can be sleeved on the sealing ring 70 and part of the inner copper sheet 111a from the outer side surface. As for the upper end sealing ring 71, the structure of the upper end sealing ring 71 combined with the copper sheet may be the structure shown in fig. 6, 8 or 9. In the structure shown in fig. 6, the first copper sheet 111 and the second copper sheet 112 are rotated 180 degrees for use, and the opening 111c is pressed by the upper surface of the uppermost intermediate seal ring 72, so that the opening 111c is prevented from opening when the upper end seal ring 71 receives the first axial pressure F1. By describing the structure shown in fig. 6 as being used for the upper end seal ring 71 and the lower end seal ring 73, respectively, it can be understood that the openings 111c should be pressed by the adjacent seal rings to prevent the openings 111c from being opened when receiving the first axial pressing force F1 or the second axial pressing force F2. The structure of fig. 8 can be realized by cladding the sealing ring 70 with copper sheets and then welding at the gap. The structure of fig. 9 is configured such that the overlapping portions of the inner copper sheets 111a and the outer copper sheets 111b are disposed on the upper surface and the lower surface of the seal ring 70, because when the overlapping portions of the inner copper sheets 111a and the outer copper sheets 111b are disposed on the inner side or the outer side of the seal ring 70, a cutting action may be applied to the adjacent seal rings during the compression process by the first axial pressure F1 or the second axial pressure F2, and the overlapping portions are disposed on the upper surface and the lower surface of the seal ring 70, and the adjacent seal rings may press the overlapping portions, thereby further isolating direct contact with small molecules of high-temperature and high-pressure steam. The structure shown in fig. 8 can be formed by welding the overlapping portions of the inner copper sheet 111a and the outer copper sheet 111b in fig. 9.

Taking FIG. 11 as an example, the structure of the lower end seal ring 71 and the copper sheet is shown in FIG. 6, when the upper end seal ring 71 bears the first axial pressure F ₁ First axial pressure force F ₁ The downward transmission and the deformation takes place for lower extreme sealing ring 73 in radial direction, distributes like this and can conflict with center tube 30 in first copper sheet 111 on the medial surface of lower extreme sealing ring 73, distributes and can conflict with sleeve pipe 40 in first copper sheet 111 on the surface of lower extreme sealing ring 73, and this can be realized through setting up the thickness to first copper sheet 111 to the sealing ring 70 that does not wrap up the copper sheet this moment seals respectively with center tube 30 and sleeve pipe 40. In one embodiment, the thickness of first copper sheet 111 is 1mm. When the structure of the upper end sealing ring 71 and the copper sheet is as shown in FIG. 8, the lower end sealing ring 71 bears the second axial pressure F ₂ In this case, the third copper plate 113 covering the shoulder formed on the upper surface of the upper end seal ring 71 is not broken. This may be accomplished by setting the thickness of the third copper sheet 113, in one embodiment, the thickness of the third copper sheet 113 is 1mm.

It is particularly emphasized that the sealing ring 70 is clad with a copper skin, and that a very high pressure is required to achieve a seal of the sealing ring 70 with the base pipe 30 and the sleeve 40, i.e. a metal-to-metal seal. In the embodiment of the subject application, including a seal ring that is not clad with copper, the seal ring is generally centered, e.g., the center seal ring 72 that is centered between three center seal rings 72 in the embodiment of FIG. 11 is not clad with copper, and the center seal ring 72 in any of the embodiments of FIG. 12 is not clad with copper. The sealing ring 70 which is not coated with the copper sheet plays a main sealing role, the lower end sealing ring 71 prevents most high-temperature high-pressure steam, and the middle sealing ring 72 at the lowest end further prevents a part of high-temperature high-pressure steam, so that the high-temperature high-pressure steam reaching the middle sealing ring 72 at the lowest end is very little, the corrosion and the degradation of the high-temperature high-pressure steam to the middle sealing ring 72 are effectively reduced, and the sealing duration time of the rubber cylinder 10 is prolonged. The number of the intermediate sealing rings 72 not covered with the copper sheet may be two or more as required. When the upper end sealing ring 71 is coated with the copper sheet, the copper sheet is mainly used to prevent the shoulder protrusion 107, please refer to the above "structural design for reducing or preventing the shoulder protrusion 107".

Referring to fig. 12, the two ends 104, 105 of the glue cartridge 10 may be leveled by the glue 109. Each seal ring 70 is annular as a whole and extends in the axial direction of the cartridge 10. When the thicknesses of the glue 109 between the adjacent bases 108 are the same, the hardness of the glue cartridge 10 in the same area can be made substantially the same as much as possible, and the glue cartridge 10 can be prevented from being locally collapsed due to uneven stress. However, when the glue cylinder 10 is three-segment type as shown in fig. 18, each segment of glue cylinder can be a single glue cylinder, so that the glue cylinder 10 shown in fig. 18 is equivalent to being formed by splicing three mutually independent glue cylinders in the axial direction. Fig. 18 shows the glue cartridge 10 as a three-segment type, but the glue cartridge may have other segments, such as two segments or five segments, in other embodiments. It should be noted that in one embodiment of the present application, the rigid spacer ring 50 may also be used between the seal rings shown in fig. 11. The inventors have found that when the seal ring 70 and the coated copper sheet are partially bulged or partially hard, the deformation of the seal ring against them is severely affected. The rigid spacer ring 50 can uniformly apply pressure to both upper and lower surfaces that are in contact with each other, thereby preventing the upper surface or the lower surface of the seal ring 70 from becoming uneven when subjected to axial pressure due to uneven hardness thereof, and preventing the upper surface or the lower surface of the adjacent seal ring from becoming uneven due to uneven hardness thereof, which is caused by uneven hardness thereof, of the seal ring 70.

Due to the mixing of the fiber filaments in the glue 109, when the glue cartridge 10 is subjected to the first axial pressure F ₁ Or second axial pressure force F ₂ While expanding in the radial direction (inward and outward), the filaments will limit the expansion, thereby increasing the structural rigidity of the cartridge 10 as a whole and increasing the compressive strength of the cartridge 10. In particular, when the base 108 is annular, the seal ring 70 is subjected to a first axial pressure F ₁ Or second axial pressure force F ₂ In this case, the force applied to each sealing ring 70 is relatively uniform, thereby preventing the partial collapse of the rubber tube 10. Also, in one embodiment of the present application, the thickness phase of the gel 109 between adjacent substrates 108In the same way, it is ensured that the first axial pressure F is applied ₁ Or second axial pressure force F ₂ The acting sealing ring 70 uniformly transmits the force, and the parts of the sealing ring 70 are prevented from being crushed due to uneven force.

Referring to fig. 12, the seal rings 70 are bonded to each other by the adhesive 109 and the sum of the lengths of the bonded seal rings 70 in the axial direction is equal to the length of the through hole 103, thereby forming a plurality of seal segments. In FIG. 5, the thickness of the substrate 108 is 1.8cm to 2.5cm, and the number of the substrates can be selected to be 2 to 12. In the embodiment of fig. 11 having 5 seal rings 70, the number of substrates 108 is also 5. The diameter of the filaments is selected to be 7-30 μm, which allows a large number of filaments to be provided on one sealing ring 70, which greatly increases the stiffness of the cartridge 10. According to the test of the inventors, the thickness of the substrate 108 is preferably not more than 2 cm. This is because the inventors found that the cement forming the gel 109 needs to penetrate into the substrate 108 to form the seal ring 70, but the penetration speed of the cement gradually becomes slower as the thickness of the substrate 108 increases. Especially when the thickness of the substrate 108 is greater than 2.5cm, the penetration speed of the glue solution will be very slow. Thus, in one embodiment, each substrate 108 has a thickness of 2cm, and in other embodiments may be 1.8cm or 2.5cm.

Referring to fig. 12 and 13, fig. 12 and 1 generally illustrate the deformation of the cartridge 10 when subjected to a first axial compressive force F1. Taking the rubber cylinder 10 shown in fig. 12 as an example, the rubber 109 is arranged between the adjacent sealing rings 70, and the rubber cylinder 10 is not subjected to the first axial pressure F ₁ Each sealing ring 70 forms an angle β with the radial direction of the rubber cylinder 10, and β is an angle of 10 ° in fig. 12. In other embodiments, β may also be a 5 ° angle or a 45 ° angle. The reason for providing β in the present application is that the sealing ring 70 as a whole is hard and is subjected to the first axial pressure F of the rated magnitude ₁ When the rubber cylinder 10 is deformed insufficiently and cannot play a role in sealing, the sealing ring 70 firstly forms an included angle beta with the radial direction of the rubber cylinder 10 to become the horizontal position of the sealing ring 70 with the radial direction of the rubber cylinder 10, and then the radial protrusion is carried out, so that the deformation degree of the rubber cylinder 10 can be improved. In the embodiment shown in fig. 11, the first axial pressure F is not applied to the rubber tube 10 ₁ While each seal ring 70 is in contact withThe radial directions of the glue cartridges 10 are parallel. As shown in fig. 1, the cartridge 10 shown in fig. 11 and 12 is subjected to a first axial compressive force F ₁ Then, both are shortened in the axial direction and expanded in the radial direction, and then the second axial pressure F is applied to the lower end seal ring 73 ₂ 。

In one embodiment of the present application, the substrate 108 is a graphite packing or a carbon fiber packing. Packing (packing) is usually woven from relatively soft threads, usually square or rectangular or circular in cross-section. In one embodiment, the cross-section of the substrate 108 is quadrilateral, such as square. In other embodiments, the cross-section of the substrate 108 may also be circular.

The constraining sheath 20 of the glue cartridge 10 will be described in detail below.

Referring to fig. 14, 15, 16 and 17, as shown in fig. 14, the constraining sheath 20 is generally flared having a flared end 22 and a necked end 21. Referring to FIG. 15, while the flared end 22 of the constraining sheath 20 is disposed over the upper and lower ends 104 and 106, in other embodiments, the flared end 22 may be disposed over only one of the upper and lower ends 104 and 106 depending primarily on whether the end is to be constrained from deforming too much during compression. In fig. 15-17, the number of constraining sleeves 20 is two, with the flared end 22 of one constraining sleeve 20 sleeved on the upper end portion 104 and the flared end 22 of the other constraining sleeve 20 sleeved on the lower end portion 106. Referring to fig. 16, the constricted end 21 of the constraining sheath 20 is away from the upper end 104 or lower end 106 sheathed by the flared end 22 for withstanding pressure from the axial direction. In fig. 15 and 16, the position relationship between the constraining sheath 20 and the rest of the rubber sleeve 10 is schematically shown only for the sake of clarity of the structure, and in fact, the constraining sheath 20 is tightly combined with the end of the rubber sleeve 10, i.e. the two are in contact with each other. As can be seen from FIG. 17, the first axial compressive force F is applied ₁ Then, the constraining sheath 20 is cylindrical as a whole. Also, the diameter of the flared end 22 and the necked end 21 of the constraining sheath 20 are substantially the same, and both are the same as the inner diameter of the sleeve 40, with the outer surface 101 of the rubber sleeve 10 sealing against the sleeve 40 and the inner surface 102 of the rubber sleeve 10 sealing against the base pipe 30.

The function of the restraining sheath 20 is described hereinThis is important because the seal ring 70 of the present application is axially disposed and pressure is applied to the seal ring 70 from the axial direction. Therefore, it is very likely that the upper end sealing ring 71 and the lower end sealing ring 72 located at both ends of the rubber cylinder 10 will be pressed by the first axial pressure F ₁ Or second axial pressure force F ₂ In the radial direction, to make a first contact with the central tube 30 and the sleeve 40, so that the intermediate sealing ring 72 cannot be radially bulged due to too small force. By the end portion of the restraining sleeve 20 being restrained, the intermediate seal ring 72 can be first raised, and after the intermediate seal ring 72 is restrained by the central tube 30 and the sleeve 40, the upper end seal ring 71 and the lower end seal ring 72 are raised radially to bring the restraining sleeve 20 into the deformation shown in fig. 15, 16 and 17. Or, first, the middle sealing ring 72 is raised first, and in the process, the upper sealing ring 71 and the lower sealing ring 72 are also raised radially and bring about the deformation of the restraining sleeve 20 as shown in fig. 15, 16 and 17. Both of the above two ways are specially designed to prevent the two ends of the rubber tube 10 from protruding in advance. When the constraining sheath 20 is present in the rubber tube 10 together with the design of the upper end portion 104 being harder, the intermediate portion 105 can be preferentially deformed in the radial direction without fail.

In the embodiment of fig. 15 and 16, the edges of the upper and

lower end portions

104, 106 are chamfered to conform to the constraining sheath 20, i.e., the upper and

lower end portions

104, 106 received by the flared end 22 are necked down to mate with the flared end 22. The design of the rubber sleeve 10 can increase the contact area between the end of the rubber sleeve 10 and the constraining sheath 20, and the designed end and the first axial pressure force F ₁ Has an included angle therebetween, thereby requiring a greater first axial compressive force F ₁ The rubber cylinder 10 can be compressed to generate deformation with rated size, and the required setting force is increased to a certain extent. As shown in fig. 17, when the first axial pressing force F is applied ₁ Thereafter, the cartridge 10 will extend radially inwardly and outwardly, and the constraining sheath 20 will expand radially within the confines of the sleeve 40 due to the constraint of the sleeve 40, and eventually the flared end 22 of the constraining sheath 20 will have substantially the same diameter as the cartridge 10 and substantially the same inner diameter as the sleeve 40. As shown in fig. 16, during compressionIn the process, a bulge is formed, and fig. 16 schematically shows a bulge 60, and the outer surface 101 of the rubber cylinder 10 is expanded outwards as a bulge in the actual compression, but the present application in one embodiment intentionally makes the bulge speed of the middle part of the rubber cylinder 10 faster than that of the two ends of the rubber cylinder through the design of the restraining sleeve 20. Importantly, if the constraining sheath 20 is selected to be a material that is not readily deformable, as shown in FIG. 16, as compression continues, the protrusion 60 will contact the upper edge of the constraining sheath 20 and eventually shear the protrusion 60, affecting the seal of the glue cartridge 10. The constraining sheath is chosen in this application as a copper sheath and defines in thickness the maximum thickness of the flared end 22, by which is meant for example the entire flared edge in fig. 14, rather than the end face furthest to the right in fig. 14, of not more than 2 mm. Such a definition can result in the constraining sheath 20 causing no damage, or less damage, to the protrusion 60. And also facilitates deformation of the constraining sheath 20 by the sleeve 40 during compression as shown in figure 17. For the same reason, it is not possible to use a right-angled type of constraining sleeve 20 as shown in FIG. 17 prior to compression, otherwise the constraining sleeve 20 would also shear the gradually convex outer surface 101 and cause a split to the rubber sleeve 10 during compression. In the present application, the constraining sheath 20 is flared such that the constraining sheath 20 and the protrusion 60 are in surface contact rather than in line contact during compression, thereby greatly reducing the possibility of damage to the protrusion 60. While, as shown in fig. 14, the necked end 21 has an inward chamfer that will surround the center tube 30 when compressed and that will receive the first axial pressure force F ₁ Such a design enables the compression sleeve 20 to be deformed orderly and gradually without being subjected to the first axial pressure force F ₁ And suddenly crushing. Another important reason for the present application's choice of the constraining sheath 20 as a copper sheath is that it is easily deformed and does not get stuck between the casings 40 when the packer 200 is tripped out of the well. For the same reason, silver, which is also easily deformable, can also be selected as the constraining sheath.

The present application also provides a packer having a packing element 10 as defined in one of the above-mentioned aspects.

The present application also provides a bridge plug having a cartridge 10 as defined in one of the above-mentioned embodiments.

Thus, it should be appreciated by those skilled in the art that while a number of exemplary embodiments of the present application have been illustrated and described in detail herein, many other variations and modifications consistent with the principles of the application may be ascertained or derived directly from the disclosure herein without departing from the spirit and scope of the application. Accordingly, the scope of the present application should be understood and interpreted to cover all such other variations or modifications.

Claims

1. A glue tube (10) having a through hole (103) in the center, an inner surface (102) at the through hole (103), an outer surface (101) corresponding to the inner surface (102), an upper end portion (104) and a lower end portion (106) at both ends of the glue tube (10), respectively, and an intermediate portion (105) between the upper end portion (104) and the lower end portion (106), the upper end portion (104) being adapted to receive a first axial pressure in an axial direction, the lower end portion (106) being adapted to receive a second axial pressure in the axial direction opposite to the first axial pressure; -when said first axial pressure is applied to said upper end portion (104), intermediate portion (105) and lower end portion (106) are deformed in a radial direction; -said upper end portion (104), intermediate portion (105) and lower end portion (106) are deformed in said radial direction when said second axial pressure is applied to said lower end portion (106),

the rubber sleeve (10) is formed by arranging an upper end sealing ring (71) at the upper end, a lower end sealing ring (73) at the lower end and more than one middle sealing ring (72) between the upper end sealing ring (71) and the lower end sealing ring (73) in the axial direction, wherein the upper end sealing ring (71) serves as the upper end part (104), the lower end sealing ring (73) serves as the lower end part (106), and the middle sealing ring (72) serves as the middle part (105);

the lower end sealing ring (73) is wrapped with a first copper sheet (111), and the first copper sheet (111) wraps the upper surface, the lower surface and the outer side surface of the lower end sealing ring (73) but does not wrap the inner side surface of the lower end sealing ring (73); the thickness of the first copper sheet (111) is set such that, when the upper end portion (104) bears the first axial pressure, the lower end sealing ring (73) deforms in the radial direction to enable the first copper sheet (111) distributed on the outer surface of the lower end sealing ring (73) to abut against the sleeve (40);

the middle sealing ring (72) is provided with a colloid (109) and an annular base body (108), the base body (108) is composed of a plurality of mutually crossed fiber filaments resistant to high temperature and high pressure, the colloid (109) is bonded with each fiber filament, and the colloid (109) is distributed on the surface of each base body (108) so that the inner part and the outer part of the plurality of sealing rings (70) arranged along the axial direction form the inner surface (102) and the outer surface (101) respectively;

the number of the middle sealing rings (72) is three or more, and the thicknesses of the colloids (109) between the adjacent substrates (108) are the same.

2. The glue cartridge (10) of claim 1,

the opening edge of the first copper sheet (111) is flush with the inner side face of the lower end sealing ring (73).

3. The glue cartridge (10) of claim 1,

a third copper sheet (113) is coated outside the upper end sealing ring (71), and the third copper sheet (113) coats the upper surface, the lower surface and the outer side surface of the upper end sealing ring (71) but does not coat the inner side surface of the upper end sealing ring (71); the third copper sheet (113) is formed so as to have a thickness such that the third copper sheet (113) covering a shoulder formed by the upper surface of the upper end seal ring (71) does not break when the lower end portion (106) receives the second axial pressure.

4. The glue cartridge (10) of claim 1,

the quantity of middle sealing ring (72) is three, wherein the lower extreme middle sealing ring (72) and the top middle sealing ring (72) all have the cladding to have the copper sheet, middle sealing ring (72) do not wrap the copper sheet.

5. The glue cartridge (10) of claim 1,

the hardness of the upper end sealing ring (71) is greater than that of the middle sealing ring (72), so that when the upper end sealing ring (71) bears the first axial pressure, the deformation of the middle sealing ring (72) in the radial direction is greater than that of the upper end sealing ring (71);

the hardness of the lower end sealing ring (73) is greater than the hardness of the middle sealing ring (72), so that when the lower end sealing ring (73) bears the second axial pressure, the deformation of the middle sealing ring (72) in the radial direction is greater than the deformation of the lower end sealing ring (73) in the radial direction.

6. The glue cartridge (10) of claim 5,

the hardness of the upper end sealing ring (71) is substantially the same as the hardness of the lower end sealing ring (73), such that when the upper end sealing ring (71) is subjected to the first axial pressure, the deformation of the middle sealing ring (72) in the radial direction is greater than the deformation of the upper end sealing ring (71) and the lower end sealing ring (73) in the radial direction, and when the lower end sealing ring (73) is subjected to the second axial pressure, the deformation of the middle sealing ring (72) in the radial direction is greater than the deformation of the upper end sealing ring (71) and the lower end sealing ring (73) in the radial direction.

7. The glue cartridge (10) of claim 1,

the matrix (108) is a graphite packing or a carbon fiber packing or a glass fiber packing.

8. A packer, characterized by comprising a packing element (10) according to any one of claims 1 to 7.

9. A bridge plug, characterized in that it comprises a cartridge (10) according to any one of claims 1 to 7.