CN213775275U - Threaded joint for pipe - Google Patents
Threaded joint for pipe Download PDFInfo
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- CN213775275U CN213775275U CN202022871324.6U CN202022871324U CN213775275U CN 213775275 U CN213775275 U CN 213775275U CN 202022871324 U CN202022871324 U CN 202022871324U CN 213775275 U CN213775275 U CN 213775275U
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Abstract
The utility model belongs to the technical field of the screwed joint for the oil casing, concretely relates to screwed joint for pipe aims at solving among the prior art deep well, the deep oil of high-pressure high corrosion, the airtight not enough problem of oil casing for gas well, and this application provides a screwed joint for pipe, including outer sleeve joint and interior sleeve joint, the contact area of interior sleeve joint and outer sleeve joint includes connecting thread district, sealing surface district and torque shoulder district. The connecting thread section adopts a buttress thread structure, so that the sealing performance of a sealing surface can be effectively ensured, and the stress concentration at a torque shoulder can be reduced; the sealing surface section is of a conical surface-to-conical surface structure, so that the sealing failure caused by the shrinkage of the front end of the inner sleeve joint and the damage of the front end surface of the inner sleeve joint can be effectively reduced; the torque shoulder section is a negative angle inverted cone structure that improves joint galling resistance and over-torquing resistance while reducing stress concentrations.
Description
Technical Field
The utility model belongs to the technical field of the screwed joint for the oil casing, concretely relates to screwed joint for pipe.
Background
The threaded connection is the main connection mode of the oil casing and is also the weakest link of the oil casing, and about 80% of failures of the oil casing occur at the threaded connection part. The API standard threaded connection mode is not enough in the aspect of guaranteeing the structural integrity and the sealing integrity of the underground pipe column, and cannot be applied to oil and gas wells in deep wells, high-pressure environments, high-corrosion environments and other harsh environments. Therefore, there is a need for a new threaded joint for pipes that solves or at least mitigates the above-mentioned problems.
SUMMERY OF THE UTILITY MODEL
In order to solve the above problems in the prior art, that is, to solve the problem of insufficient air sealing of the oil casing for the deep well, the high-pressure high-corrosion deep oil and the gas well in the prior art, the present application provides, on one hand, a threaded joint for a pipe, which includes an inner casing joint and an outer casing joint, wherein the inner casing joint includes a first structure portion, a second structure portion and a third structure portion which are sequentially connected; the outer sleeve joint comprises a fourth structure part, a fifth structure part and a sixth structure part which are connected in sequence;
the first structure part is provided with a buttress external thread; the fourth structure part is provided with a buttress internal thread matched with the buttress external thread;
the inner sleeve pipe joint and the outer sleeve pipe joint are screwed together:
the outer surface of the second structure part, which is close to the third structure part, is tightly attached to the inner surface of the fifth structure part, and the outer surface of the second structure part, which is close to the first structure part, and the inner surface of the fifth structure part form a first annular space;
the third structure part and the sixth structure form a second annular space.
The application also provides a threaded joint for a pipe, which comprises an outer sleeve joint and an inner sleeve joint, wherein the periphery of the inner sleeve joint comprises a buttress external thread, an inner sleeve joint sealing section and an inner sleeve joint torque shoulder section which are sequentially connected; the inner periphery of the outer sleeve joint comprises a buttress internal thread, an outer sleeve joint sealing section and an outer sleeve joint torque shoulder section which are sequentially connected;
the inner sleeve joint sealing section comprises a first inner tube sealing part, a second inner tube sealing part and a third inner tube transition part which are sequentially connected, the first inner tube sealing part is connected with the end part of the buttress external thread, the third inner tube transition part is connected with the inner sleeve joint torque shoulder section, and the second inner tube sealing part is of an inclined structure which continuously reduces towards the third inner tube transition part;
the outer sleeve joint sealing section comprises a first outer tube sealing part, a second outer tube sealing part and a third outer tube transition part which are sequentially connected, the first outer tube sealing part is connected with the end part of the buttress internal thread, the third outer tube transition part is connected with the outer sleeve joint torque shoulder section, and the second outer tube sealing part is an inclined structure which continuously reduces towards the third outer tube transition part;
under the fastening state of the inner sleeve joint and the outer sleeve joint, the buttress external threads and the buttress internal threads are screwed and matched to form a connecting thread area, the sealing section of the inner sleeve joint and the sealing section of the outer sleeve joint form a sealing surface area relatively, and the torque shoulder section of the inner sleeve joint and the torque shoulder section of the outer sleeve joint form a torque shoulder area relatively; the second outer tube sealing portion is smaller than the second inner tube sealing portion along the axial length, the second inner tube sealing portion is tightly abutted to the second outer tube sealing portion to form a sealing section, an oil storage groove is formed between the first outer tube sealing portion and the first inner tube sealing portion, and a vortex releasing space is formed between the third outer tube transition portion and the third inner tube transition portion.
In some preferred technical solutions, the thread taper of the buttress external thread and the thread taper of the buttress internal thread are both 1: 16.
In some preferred technical solutions, the buttress external thread includes a plurality of thread teeth, and the thread teeth include a bearing surface and a guide surface;
the included angle between the bearing surface and the vertical line of the thread axis is alpha, and alpha belongs to (-3 degrees and 30 degrees);
the angle between the guide surface and the perpendicular to the thread axis is beta, beta epsilon (3 degrees, 36 degrees).
In some preferable technical schemes, the buttress external thread and the buttress internal thread are in transition fit, and the thread flank fit tolerance of the buttress external thread and the buttress internal thread is a, and a is (-0.05mm, 0.05 mm).
In some preferred technical solutions, the clearance between the crest of the buttress external thread and the root of the buttress internal thread is b, b e (0.04mm, 0.1 mm).
In some preferred embodiments, the first annulus is a sump having an axial length greater than one pitch and less than two pitches.
In some preferred embodiments, the second structure portion and the fifth structure portion each include a tapered surface having a taper p, p e (5 °, 20 °).
In some preferred technical solutions, the radial fit between the tapered surface of the second structural portion and the tapered surface of the fifth structural portion is an interference fit, and the sealing radial interference is d, d e (0.1mm, 0.6 mm).
In some preferred embodiments, the amount of radial clearance between the third feature and the sixth feature is h, h e (0.5mm, 0.8 mm).
In some preferred technical solutions, the outer sleeve joint is provided with an outer sleeve shoulder chamfer, the inner sleeve joint is provided with an inner sleeve shoulder chamfer, and the outer sleeve shoulder chamfer is smaller than the inner sleeve shoulder chamfer.
The utility model has the advantages that:
the utility model discloses a pipe is with special screwed joint includes endotheca coupling and outer casing pipe joint two parts, and endotheca coupling and outer casing pipe joint's contact area includes connecting thread district, sealing surface district and torque shoulder district. The angle design and the matching size of the bearing surface and the guide surface can effectively ensure the sealing performance of the sealing surface and reduce the stress concentration at the torque shoulder; the sealing surface section is of a conical surface-to-conical surface structure, the structure is close to the buttress thread end and far away from the torque shoulder end, and sealing failure caused by the shrinkage of the front end of the inner sleeve joint and the damage of the front end surface of the inner sleeve joint can be effectively reduced; the torque shoulder section is of a negative-angle inverted cone structure, and chamfers with different sizes are arranged at corners of the torque shoulder section, so that the chamfers with different sizes can improve the anti-galling and anti-over-torsion performances of the joint and reduce stress concentration. The special threaded joint is suitable for casings for deep wells, high-pressure and high-corrosion deep oil wells and gas wells.
Drawings
Other features, objects and advantages of the present application will become more apparent upon reading of the following detailed description of non-limiting embodiments thereof, made with reference to the accompanying drawings in which:
fig. 1 is a schematic view of an overall structure of a threaded joint for pipes according to an embodiment of the present invention;
FIG. 2 is an enlarged view of A in FIG. 1;
FIG. 3 is an enlarged partial view of the connection thread region B of FIG. 2;
FIG. 4 is an enlarged partial view of the connecting thread region C of FIG. 2;
FIG. 5 is an enlarged view of the seal panel of FIG. 2;
FIG. 6 is an enlarged view of the torque shoulder region of FIG. 2;
FIG. 7 is an enlarged view of the front end of the inner sleeve joint according to an embodiment of the present invention;
FIG. 8 is an enlarged schematic view of the inner stop end of the outer sleeve joint in an embodiment of the present invention;
list of reference numerals:
1-inner sleeve joint; 2-outer casing pipe joint; 3-connecting the threaded zone; 4-sealing surface area; 5-torque shoulder area; 6-buttress external threads; 7-buttress internal threads; 8-a bearing surface; 9-a guide surface; 10-buttress external thread tooth crest; 11-buttress internal thread roots; 12-an oil storage tank; 13-sealing the conical surface; 14-a second inner tube seal; 15-a second outer tube seal; 16-shoulder transition zone; 17-chamfering of shoulders; 18-shoulder surface; 19-vortex relief space; 20-inner casing joint torque shoulder transition zone; 21-outer sleeve joint torque shoulder transition zone; 22-chamfering the shoulder of the inner sleeve; 23-chamfering the shoulder of the outer sleeve; 24-front end of inner sleeve joint; an alpha-bearing surface angle; beta-guide surface angle; gamma-shoulder angle; a-thread flank fit tolerance; b-the clearance between the tooth root and the tooth top; c-axial length of the sealing conical surface; d-radial interference magnitude of the sealing conical surface; e-axial length of shoulder transition zone; f-length of front end of inner sleeve joint
Detailed Description
In order to make the embodiments, technical solutions and advantages of the present invention more obvious, the technical solutions of the present invention will be described clearly and completely with reference to the accompanying drawings. It should be understood by those skilled in the art that these embodiments are only for explaining the technical principle of the present invention, and are not intended to limit the scope of the present invention.
The utility model discloses a threaded joint for pipe, which comprises an inner sleeve joint and an outer sleeve joint, wherein the inner sleeve joint comprises a first structure part, a second structure part and a third structure part which are connected in sequence; the outer sleeve joint comprises a fourth structure part, a fifth structure part and a sixth structure part which are connected in sequence;
the first structure part is provided with a buttress external thread; the fourth structure part is provided with a buttress internal thread matched with the buttress external thread;
the inner sleeve pipe joint and the outer sleeve pipe joint are screwed together:
the outer surface of the second structure part, which is close to the third structure part, is tightly attached to the inner surface of the fifth structure part, and the outer surface of the second structure part, which is close to the first structure part, and the inner surface of the fifth structure part form a first annular space;
the third structure part and the sixth structure form a second annular space.
In a preferred embodiment of the present application, the first structural portion is a buttress-shaped external thread section, the second structural portion is an inner box joint sealing section, and the third structural portion is an inner box joint torque shoulder section; the fourth structure part is a buttress internal thread section, the fifth structure part is an outer sleeve joint sealing section, and the sixth structure part is an outer sleeve joint torque shoulder section;
and under the screwing state of the inner sleeve joint and the outer sleeve joint, the outer pipe surface of the inner sleeve joint sealing section close to the torque shoulder section of the inner sleeve joint is tightly attached to the inner pipe surface of the outer sleeve joint sealing section, and the outer pipe surface of the inner sleeve joint sealing section close to the buttress outer thread section and the inner pipe surface of the outer sleeve joint sealing section form a first annular space.
Specifically, the inner sleeve joint sealing section comprises a first inner tube sealing part, a second inner tube sealing part and a third inner tube transition part which are sequentially connected, the first inner tube sealing part is connected with the end part of the buttress external thread, the third inner tube transition part is connected with the inner sleeve joint torque shoulder section, and the second inner tube sealing part is of an inclined structure which continuously reduces towards the third inner tube transition part; the first inner pipe sealing part is the outer pipe surface of the second structure part close to the first structure part; the third inner tube transition part is the outer tube surface of the second structure part close to the third structure part.
The outer sleeve joint sealing section comprises a first outer tube sealing part, a second outer tube sealing part and a third outer tube transition part which are sequentially connected, the first outer tube sealing part is connected with the end part of the buttress internal thread, the third outer tube transition part is connected with the outer sleeve joint torque shoulder section, and the second outer tube sealing part is an inclined structure which continuously reduces towards the third outer tube transition part;
under the fastening state of the inner sleeve joint and the outer sleeve joint, the buttress external threads are screwed and matched with the buttress internal threads to form a connecting thread area, the sealing section of the inner sleeve joint and the sealing section of the outer sleeve joint form a sealing surface area relatively, and the torque shoulder section of the inner sleeve joint and the torque shoulder section of the outer sleeve joint form a torque shoulder area relatively; the second outer tube sealing portion is smaller than the second inner tube sealing portion and the second inner tube sealing portion along the axial length, the second outer tube sealing portion is tightly abutted to form a sealing section, a first annular space is formed between the first outer tube sealing portion and the first inner tube sealing portion, namely, an oil storage tank, and a second annular space is formed between the third outer tube transition portion and the third inner tube transition portion, namely, a vortex releasing space.
The utility model discloses optimize the structure and the parameter of connecting thread, sealed face and moment of torsion circular bead on special screwed joint's at home and abroad basis to reduce stress concentration, guarantee sealing performance, reduce plastic deformation, thereby guarantee oil sheathed tube structural integrity and sealed integrality. In order to more clearly explain the threaded joint for pipes of the present invention, a preferred embodiment of the present invention will be described in detail below with reference to the accompanying drawings.
As a preferred embodiment of the present invention, the threaded joint for pipes of the present invention is shown in fig. 1, and comprises an outer sleeve joint 2 and an inner sleeve joint 1, wherein the inner sleeve joint is formed at one end of an oil pipe, and the outer sleeve joint is disposed outside the outer sleeve joint for sealing and connecting a next oil pipe or joint. The periphery of the inner sleeve joint 1 comprises a buttress external thread 6, an inner sleeve joint sealing section and an inner sleeve joint torque shoulder section which are sequentially connected; the outer sleeve joint comprises a buttress internal thread 7, an outer sleeve joint sealing section and an outer sleeve joint torque shoulder section which are sequentially connected within 2 weeks.
Furthermore, the inner sleeve joint sealing section comprises a first inner tube sealing part, a second inner tube sealing part and a third inner tube transition part which are sequentially connected, the first inner tube sealing part is connected with the tooth root of the end part of the buttress external thread 6, the third inner tube transition part is connected with the torque shoulder section of the inner sleeve joint, and the second inner tube sealing part is of an inclined structure which continuously reduces towards the direction of the third inner tube transition part; namely, the radial direction of the first inner tube sealing part is larger than that of the third inner tube sealing surface, and the second inner tube sealing part is a sealing conical surface.
The outer tube head sealing section comprises a first outer tube sealing part, a second outer tube sealing part and a third outer tube transition part which are connected in sequence, the first outer tube sealing part is connected with the tooth root of the 7 end part of the buttress internal thread, the third outer tube transition part is connected with the outer tube head torque shoulder section, the second outer tube sealing part is of an inclined structure which continuously reduces towards the third outer tube transition part, namely, the radial direction of the first outer tube sealing part is larger than that of the third outer tube transition part, and the second outer tube sealing part is a sealing conical surface. Preferably, the first outer tube seal portion includes a first surface of curvature, the second outer tube seal portion includes a sealing cone surface, and the third outer tube transition includes a third surface of curvature. The thread teeth at the tail ends of the buttress external threads are connected with the first inner pipe sealing part, and the tooth tops of the thread teeth are obliquely arranged. Further, the crests of the buttress external threads are gradually increased in the axial direction and decreased at the distal ends.
In the fastened state of the inner and outer casing joints 1 and 2, the contact area of the inner and outer casing joints 1 and 2 is mainly composed of three sections, namely a connecting thread area 3, a sealing surface area 4 and a torque shoulder area 5. The buttress external threads 6 and the buttress internal threads 7 are screwed and matched to form a connecting thread area 3, the sealing section of the inner sleeve joint and the sealing section of the outer sleeve joint form a sealing surface area 4 relatively, and the torque shoulder section of the inner sleeve joint and the torque shoulder section of the outer sleeve joint form a torque shoulder area 5 relatively. Wherein, the connecting thread area 3 is of a buttress thread structure; the sealing surface area 4 is a conical surface-to-conical surface structure; the torque shoulder region 5 is of a negative angle inverted cone structure. The threaded joint for the pipe is of an air-tight special threaded structure and is suitable for casings for deep wells, high-pressure and high-corrosion deep oil wells and gas wells.
Further, the area of the second outer pipe sealing part is smaller than that of the second inner pipe sealing part, namely the axial length of the second outer pipe sealing part is smaller than that of the second inner pipe sealing part, through the arrangement, the radial direction of the third outer pipe transition part is larger than that of the third inner pipe transition part, and a gap is formed between the third outer pipe transition part and the third inner pipe transition part. When the inner sleeve joint 1 and the outer sleeve joint 2 are fastened, the second inner tube sealing portion 14 and the second outer tube sealing portion 15 are tightly abutted to form a sealing section, a gap is formed between the first outer tube sealing portion and the first inner tube sealing portion, the gap is an oil storage tank 12, and a gap between the third outer tube transition portion and the third inner tube transition portion is a torque shoulder eddy current release space 19. One end of the first outer pipe sealing part is connected with the tooth root of the end part of the buttress internal thread, and the other end of the first outer pipe sealing part is connected with the second outer pipe sealing part; one end of the first inner pipe sealing part is connected with the tooth root of the buttress external thread, and the other end of the first inner pipe sealing part is connected with the second inner pipe sealing part, so that a gap exists between the first outer pipe sealing part and the first inner pipe sealing part, and the gap forms an oil storage tank 12. The third inner tube transition is radially smaller than the third outer tube transition, and therefore a gap is formed between the third outer tube transition and the third inner tube transition, which is a torque shoulder vortex relief space 19.
Preferably, referring to fig. 3 and 4, the buttress external threads 6 and the buttress internal threads 7 in the connecting threaded zone 3 are buttress threads with a buttress thread taper of 1: 16.
Further, the buttress external thread 6 comprises a plurality of thread teeth, and the thread teeth comprise a bearing surface 8 and a guide surface 9; in a preferred embodiment of the invention, the angle between the bearing surface 8 and the perpendicular to the axis of the thread is negative, in particular the angle between the bearing surface 8 and the perpendicular to the axis of the thread is α, α ∈ (-3 °, 30 °); the negative angle load bearing surface can withstand higher compressive load performance. The lower limit value of the angle alpha is not lower than-3 degrees, and according to finite element analysis, when the lower limit value is lower than the value, the performance of the thread for bearing the compression load is reduced; the upper limit value is not higher than-30 degrees, and when the upper limit value is higher than the lower limit value, the processing difficulty is increased, and the tolerance is difficult to guarantee.
Likewise, the angle between the guide surface 9 and the perpendicular to the thread axis is β, β e (3 °, 36 °). The lower limit value is not easy to be lower than 3 degrees, when the lower limit value is lower than the lower limit value, the processing difficulty is increased, and the tolerance is difficult to guarantee; the upper limit value is not easily higher than 36 deg., and when higher than this value, the thread is degraded in its ability to withstand tensile and compressive loads.
The buttress external thread 6 and the buttress internal thread 7 are in transition fit, the thread flank fit of the bearing surface 8 and the guide surface 9 is in transition fit, the thread flank fit tolerance of the buttress external thread 6 and the buttress internal thread 7 is a, and a is larger than (-0.05mm, 0.05 mm). Tolerance a is controlled at 0.1mm, so that the thread is more economic, the machining efficiency is improved, the tool loss is reduced, the batch production is facilitated, and thread gluing in the thread-removing process is avoided.
The fit clearance fit of the thread flanks of the bearing surface 8 and the guide surface 9 is a transition fit, which can prevent the inner sleeve joint 1 and the outer sleeve joint 2 from axial displacement due to compression or tensile load, thereby ensuring the sealing performance of the sealing conical surface 13. Meanwhile, the compression load performance of the threaded joint can be improved through transition fit, and according to finite element analysis, the pressure load of the torque shoulder 16 can be reduced, and the stress concentration at the torque shoulder can be reduced.
There is a clearance between the buttress male thread crest 10 and the buttress female thread root 11, preferably a clearance b, b e (0.04mm, 0.1 mm).
Referring to fig. 5, the sealing surface section 4 includes a reservoir 12 and a sealing cone 13. The second outer tube sealing portion 15 and the second inner tube sealing portion 14 have a taper-to-taper structure, and both taper surfaces have the same taper, and the taper of the taper surface is p, and p is epsilon (5 degrees, 20 degrees). Namely, the sealing conical surface 14 of the inner sleeve joint seals the sealing conical surface 15 of the outer sleeve joint, the sealing taper is not easy to be too small, and if the taper is too small, the scratch on the sealing surface is increased due to the sliding of screwing on or unscrewing for multiple times; the seal taper is not likely to be too great, and if the taper is too great, the seal will fail due to the compressive load. In the fastening state of the inner pipe joint and the outer pipe joint, the second outer pipe sealing portion 15 is in close contact with the second inner pipe sealing portion 14 in a surface contact manner, so as to form a sealing section, i.e., a sealing conical surface 13 as shown in the figure. The axial length c of the sealing taper surface 13 is 4mm to 6mm, and after the end-piecing is tightened, there is at least a substantial contact area of 2mm or more to ensure the sealing performance of the sealing surface. Preferably, the midpoint of the sealing taper is a midpoint in the tube axis direction of the second inner tube sealing portion.
Further, an oil reservoir 12 is provided between the thread and the sealing cone 13 on the inner surface of the buttress thread 7. The axial length of the reservoir 12 is greater than one pitch and less than two pitches. In the preferred embodiment of the present invention, the axial length of the oil storage tank is controlled mainly by making the sealing conical surface 13 as close to the thread as possible, which can effectively prevent the sealing conical surface 13 from being scratched during transportation or transportation.
The sealing cone 13 is located immediately adjacent to the sump 12 and away from the torque shoulder area, and if the sealing cone 13 is located immediately adjacent to the torque shoulder area, when the inner sleeve joint 1 is subjected to external pressure, the radial dimension of the inner sleeve joint torque shoulder transition area 16 will decrease, creating a gap between the sealing surfaces, which can lead to leakage.
In some preferred embodiments, the radial fit of the sealing cone 13 is an interference fit, that is, the radial fit of the second outer tube sealing portion 15 and the second inner tube sealing portion 14 is an interference fit, and the sealing radial interference is d, d e (0.1mm, 0.6 mm). When the shoulders of the buttress external threads and the buttress internal threads are in contact, the two sealing cones are brought into intimate contact over the entire circumference to form a face-to-face seal.
Further, in some embodiments, referring to fig. 6, the torque shoulder region 5 includes a shoulder transition region 16, a shoulder chamfer 17, and a shoulder surface 18. The shoulder transition 16 includes a third inner tube transition and a third outer tube transition, namely an inner sleeve joint torque shoulder transition 20 as shown in fig. 7 and an outer sleeve joint torque shoulder transition 21 as shown in fig. 8, both of which are cylindrical in configuration. The female end is shown schematically in FIG. 8 as the forward end of the torque shoulder region of the outer sleeve joint.
The radial clearance between the transition part of the third outer pipe and the transition part of the third inner pipe is h, and h belongs to (0.5mm, 0.8 mm). This radial clearance is the torque shoulder vortex relief space 19. The vortex relief space 19 reduces erosion of the sealing cone 13 by the fluid.
More preferably, the axial length e of the shoulder transition region 16 is about 25% to 35% of the length f of the front end 24 of the inner sleeve joint, so that the torque shoulder vortex releasing space 19 is obtained and the effectiveness of the sealing cone 13 is ensured.
Torque shoulder area still includes circular bead chamfer 18, and circular bead chamfer 18 sets up not unidimensional chamfer, and specifically, outer tube joint is provided with outer tube shoulder chamfer 23, and interior tube joint is provided with interior sleeve pipe shoulder chamfer 22, and outer tube shoulder chamfer 23 is less than interior sleeve pipe shoulder chamfer 22. Preferably, the chamfer 22 of the inner sleeve shoulder is 0.9 mm-1 mm, and the chamfer 23 of the outer sleeve shoulder is 0.8 mm-0.9 mm, and according to finite element analysis, chamfers with different sizes can greatly reduce stress concentration in the interval.
The shoulder surface 18 is a negative angle inverted cone structure, and the angle gamma of the shoulder surface is 5-10 degrees. The negative angle is not easy to be too large, and if the angle is too large, the stress concentration of the shoulder of the outer sleeve joint 2 is caused, the rigidity is reduced, and the compression resistance is reduced.
In the technical solution in the embodiment of the present application, at least the following technical effects and advantages are provided:
the utility model discloses a pipe is with special screwed joint, in the application, when receiving the axial and draw the compression load, or receive axial tension and radial external pressure's combined load, or receive axial compression and internal tension's combined load, this screwed joint has good screw thread integrality and sealed integrality for outside and internal pressure.
The utility model discloses a pipe is with special screwed joint includes endotheca coupling and outer casing pipe joint two parts, and endotheca coupling and outer casing pipe joint's contact area includes connecting thread district, sealing surface district and torque shoulder district. The angle design and the matching size of the bearing surface and the guide surface can effectively ensure the sealing performance of the sealing surface and reduce the stress concentration at the torque shoulder; the sealing surface section is of a conical surface-to-conical surface structure, the structure is close to the buttress thread end and far away from the torque shoulder end, and sealing failure caused by the shrinkage of the front end of the inner sleeve joint and the damage of the front end surface of the inner sleeve joint can be effectively reduced; the torque shoulder section is of a negative-angle inverted cone structure, and chamfers with different sizes are arranged at corners of the torque shoulder section, so that the chamfers with different sizes can improve the anti-galling and anti-over-torsion performances of the joint and reduce stress concentration. The special threaded joint is suitable for casings for deep wells, high-pressure and high-corrosion deep oil wells and gas wells.
It should be noted that in the description of the present invention, the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc. indicating the directions or positional relationships are based on the directions or positional relationships shown in the drawings, which are only for convenience of description, and do not indicate or imply that the device or element must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
Furthermore, it should be noted that, in the description of the present invention, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meaning of the above terms in the present invention can be understood by those skilled in the art according to specific situations.
The terms "comprises," "comprising," or any other similar term are intended to cover a non-exclusive inclusion, such that a process, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, article, or apparatus.
So far, the technical solution of the present invention has been described with reference to the preferred embodiments shown in the drawings, but it is easily understood by those skilled in the art that the scope of the present invention is obviously not limited to these specific embodiments. Without departing from the principle of the present invention, a person skilled in the art can make equivalent changes or substitutions to the related technical features, and the technical solutions after these changes or substitutions will fall within the protection scope of the present invention.
Claims (10)
1. A threaded joint for a pipe is characterized by comprising an inner sleeve joint and an outer sleeve joint, wherein the inner sleeve joint comprises a first structure part, a second structure part and a third structure part which are sequentially connected; the outer sleeve joint comprises a fourth structure part, a fifth structure part and a sixth structure part which are connected in sequence;
the first structure part is provided with a buttress external thread; the fourth structure part is provided with a buttress internal thread matched with the buttress external thread;
the inner sleeve pipe joint and the outer sleeve pipe joint are screwed together:
the outer surface of the second structure part, which is close to the third structure part, is tightly attached to the inner surface of the fifth structure part, and the outer surface of the second structure part, which is close to the first structure part, and the inner surface of the fifth structure part form a first annular space;
the third structure part and the sixth structure form a second annular space.
2. A threaded joint for pipes as set forth in claim 1 wherein the taper of the buttress external threads and the taper of the buttress internal threads are each 1: 16.
3. A threaded joint for pipes as set forth in claim 2 wherein the buttress external threads comprise a plurality of thread teeth, the thread teeth comprising a back-up surface and a guide surface;
the included angle between the bearing surface and the vertical line of the thread axis is alpha, and alpha belongs to (-3 degrees and 30 degrees);
the angle between the guide surface and the perpendicular to the thread axis is beta, beta epsilon (3 degrees, 36 degrees).
4. A threaded joint for pipes as set forth in claim 3 wherein the buttress external thread and the buttress internal thread are transition fit and the thread flank fit tolerance of the buttress external thread and the buttress internal thread is a, a e (-0.05mm, 0.05 mm).
5. A threaded joint for pipes as set forth in claim 1 wherein the clearance between the crest of the buttress male thread and the root of the buttress female thread is b, b e (0.04mm, 0.1 mm).
6. A threaded joint for pipes as set forth in claim 1 wherein the first annular space is a sump having an axial length greater than one thread pitch and less than two thread pitches.
7. A threaded joint for pipes as set forth in claim 1 wherein the second and fifth features each comprise a taper having a taper p, p e (5 °, 20 °).
8. A threaded joint for pipes as set forth in claim 7 wherein the radial fit of the tapered surfaces of the second and fifth features is an interference fit with a radial seal interference of d e (0.1mm, 0.6 mm).
9. A threaded joint for pipes as set forth in claim 1 wherein the amount of radial clearance of the third feature from the sixth feature is h, h e (0.5mm, 0.8 mm).
10. A threaded joint for pipes as set forth in claim 1 wherein the outer sleeve joint is provided with an outer sleeve shoulder chamfer and the inner sleeve joint is provided with an inner sleeve shoulder chamfer, the outer sleeve shoulder chamfer being less than the inner sleeve shoulder chamfer.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202022871324.6U CN213775275U (en) | 2020-12-02 | 2020-12-02 | Threaded joint for pipe |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202022871324.6U CN213775275U (en) | 2020-12-02 | 2020-12-02 | Threaded joint for pipe |
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| Publication Number | Publication Date |
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| CN213775275U true CN213775275U (en) | 2021-07-23 |
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| CN202022871324.6U Active CN213775275U (en) | 2020-12-02 | 2020-12-02 | Threaded joint for pipe |
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|---|---|
| CN (1) | CN213775275U (en) |
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2020
- 2020-12-02 CN CN202022871324.6U patent/CN213775275U/en active Active
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