CN110608321A - Double-line marine riser joint - Google Patents
Double-line marine riser joint Download PDFInfo
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- CN110608321A CN110608321A CN201910814009.9A CN201910814009A CN110608321A CN 110608321 A CN110608321 A CN 110608321A CN 201910814009 A CN201910814009 A CN 201910814009A CN 110608321 A CN110608321 A CN 110608321A
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- 238000000034 method Methods 0.000 claims description 6
- 230000007423 decrease Effects 0.000 claims description 5
- 210000001503 joint Anatomy 0.000 abstract description 2
- 238000003754 machining Methods 0.000 description 7
- 238000009826 distribution Methods 0.000 description 6
- 238000007789 sealing Methods 0.000 description 6
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000005520 cutting process Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 230000009466 transformation Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
- F16L15/00—Screw-threaded joints; Forms of screw-threads for such joints
- F16L15/001—Screw-threaded joints; Forms of screw-threads for such joints with conical threads
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
- F16L15/00—Screw-threaded joints; Forms of screw-threads for such joints
- F16L15/04—Screw-threaded joints; Forms of screw-threads for such joints with additional sealings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
- F16L15/00—Screw-threaded joints; Forms of screw-threads for such joints
- F16L15/06—Screw-threaded joints; Forms of screw-threads for such joints characterised by the shape of the screw-thread
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
- F16L15/00—Screw-threaded joints; Forms of screw-threads for such joints
- F16L15/08—Screw-threaded joints; Forms of screw-threads for such joints with supplementary elements
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Non-Disconnectible Joints And Screw-Threaded Joints (AREA)
- Earth Drilling (AREA)
Abstract
The invention relates to a double-line marine riser joint, which comprises a male joint and a female joint which are matched with each other; the external taper thread of the male joint comprises a male joint equal-tooth-width thread section and a male joint variable-tooth-width thread section, wherein the male joint equal-tooth-width thread section is close to the small end face, the male joint variable-tooth-width thread section is far away from the small end face, the tooth width of the thread of the male joint equal-tooth-width thread section is unchanged, and the tooth width of the thread of the male joint variable-tooth-width thread section is linearly reduced; the inner taper thread of the female joint comprises a female joint equal-tooth-width thread section and a female joint variable-tooth-width thread section, wherein the female joint equal-tooth-width thread section is close to the large end face, the female joint variable-tooth-width thread section is far away from the large end face, the tooth width of the female joint equal-tooth-width thread section is unchanged, and the tooth width of the female joint variable-tooth-width thread section is linearly reduced. The double-line marine riser joint has the advantages of easy butt joint of threads, difficulty in loosening, uniform stress of threads and strong bearing capacity.
Description
Technical Field
The present invention relates to a pipe joint, in particular a two-wire marine riser joint.
Background
The marine riser that uses in the offshore oil development is mostly the segmental riser, and the riser is connected through the joint, and current riser joint main form comprises torque shoulder, sealing part and connecting thread triplex. In the deep sea, the marine riser receives the influence of stormy waves, and the screw thread takes place to become flexible easily and the screw thread is difficult to the income knot to cause the not enough of leakproofness and joint strength and the screw thread damage that the difficult make-up of screw thread leads to. The marine riser joint is connected through the screw thread, no matter be single shoulder connection or double shoulder connection, and the screw thread atress is all inhomogeneous, and the deep sea condition is complicated, and the riser easily receives alternating load's influence, has consequently had higher requirement to the bearing capacity of screw thread.
Disclosure of Invention
The invention aims to overcome the defects and provide a double-line marine riser joint, which mainly solves the problems of low buckling speed, uneven stress on joint threads, weak bearing capacity and the like of the traditional marine riser.
The purpose of the invention is realized as follows:
a double-line marine riser joint comprises a male joint and a female joint which are matched with each other; the male connector is provided with a double-head external taper thread, and a small end face and a main shoulder face are also arranged on the male connector; the female joint is provided with double-end inner tapered threads, the male joint is also provided with a large end face and an auxiliary shoulder face, and the thread lengths of the outer tapered threads of the male joint and the inner tapered threads of the female joint are both L;
the external taper thread of the male joint comprises a male joint equal-tooth-width thread section and a male joint variable-tooth-width thread section, wherein the male joint equal-tooth-width thread section is close to the small end face, the male joint variable-tooth-width thread section is far away from the small end face, the length of the male joint equal-tooth-width thread section is 1/2L-3/5L, the tooth width of the thread of the male joint equal-tooth-width thread section is unchanged, and the tooth width of the thread of the male joint variable-tooth-width thread section is linearly reduced;
the inner cone thread of the female joint comprises a female joint equal-tooth-width thread section and a female joint variable-tooth-width thread section, wherein the female joint equal-tooth-width thread section is close to the large end face, the female joint variable-tooth-width thread section is far away from the large end face, the length of the female joint equal-tooth-width thread section is 1/2L-3/5L, the tooth width of the female joint equal-tooth-width thread section is unchanged, and the tooth width of the female joint variable-tooth-width thread section is linearly reduced.
Furthermore, a certain gap exists between the tooth crest of the outer cone thread and the tooth bottom of the inner cone thread, and a gap exists between the tooth bottom of the outer cone thread and the tooth crest of the inner cone thread.
Further, the clearance f is 0.3-0.4 mm.
Furthermore, the bearing angle of the bearing surfaces of the male joint and the female joint is a negative bearing angle alpha, the alpha is-3 to-5 degrees, the guide angle beta of the guide surface is 40 to 45 degrees, and the screw pitch is 12.7 mm; the tooth height is 3.0 mm-5.0 mm.
Furthermore, on the same thread line, a first bearing surface of the female joint and a first guide surface of the female joint are connected through a tooth crest, a female joint groove is formed between the first bearing surface of the female joint and a second guide surface of the female joint on the adjacent thread line, and the bottom of the female joint groove is a tooth bottom; the taper directions of the tooth top and the tooth bottom are consistent with the taper direction of the female joint thread and are both 1: 16.365.
Furthermore, the linear reduction of the tooth width of the thread of the variable tooth width threaded section of the male joint and the linear reduction of the tooth width of the thread of the variable tooth width threaded section of the female joint are reduced by delta u, and the delta u is 0.05-0.08 mm.
Furthermore, in the assembling process of the male connector and the female connector, when the bearing surfaces of the middle threads are contacted, the bearing surfaces of the threads on the two sides are not contacted, the gap is gradually enlarged, and along with the increase of the number of turns of the screwing-on, the gap between the corresponding bearing surfaces of the threads begins to be reduced and contacted.
Furthermore, two sides of the main shoulder surface are respectively provided with an annular groove and two grooves which are uniformly distributed, the grooves are formed inwards on the outer surface of the male connector, the annular grooves are formed inwards on the inner edge of the main shoulder surface of the male connector, a sealing ring is arranged in each annular groove, a locking block is arranged in each groove, the male connector and the locking block are connected through screws, and the locking blocks are in contact with the small end surfaces of the female connector.
Furthermore, the surfaces of the locking block, which are contacted with the small end surfaces of the female joint, are provided with sawtooth belts which are matched with each other.
Compared with the prior art, the invention has the beneficial effects that:
the invention relates to a double-line marine riser joint which comprises a double-line taper pipe thread male joint and a double-line taper pipe thread female joint, wherein the load bearing angle of the double-line taper pipe thread male joint is negative, the thread tooth width of the external thread of the male joint at a position (1/2L-3/5L) close to a small end face is unchanged, and the thread tooth widths of the other threads are linearly reduced; the tooth width of the internal thread of the female joint is unchanged at the position (1/2L-3/5L) close to the large end face, and the tooth widths of the other threads are linearly reduced; in the process of screwing on, when the bearing surfaces of the middle threads are contacted, certain gaps exist between the bearing surfaces of the threads at the two sides, and the bearing surfaces are gradually enlarged. According to the invention, a certain gap exists between the tooth crest of the outer cone thread and the tooth bottom of the inner cone thread, and a certain gap exists between the tooth bottom of the outer cone thread and the tooth crest of the inner cone thread, so that the number of hand tightening turns can be increased to the maximum extent during fastening, and the number of machine tightening turns can be reduced; the male connector and the female connector are locked through the locking block, and after the upper buckle is finished, the sealing ring is in interference fit with the connector to realize sealing. Through the negative bearing angle and the variable tooth width thread, the bearing capacity of a single thread tooth is effectively improved, meanwhile, the thread tooth is uniformly loaded, and the bearing capacity of the thread is greatly improved. Therefore, the double-line marine riser joint has the advantages of easy butt joint of threads, difficult loosening, uniform stress of threads and strong bearing capacity.
Drawings
Fig. 1 is an axial sectional view of a double-line marine riser joint according to the present invention after being fastened.
Fig. 2 shows a connection state of the thread after the double-line marine riser joint is fastened.
FIG. 3 is a schematic view showing the connection state of the male connector and the female connector in the case of manual pretensioning.
FIG. 4 is a schematic view of the female connector after secondary processing.
FIG. 5 is a schematic view of the stock removal on the load flank of the box thread during secondary machining.
Fig. 6 is a partially enlarged view of fig. 5.
FIG. 7 is a schematic view of the male and female connectors after secondary processing.
FIG. 8 is a schematic view of a male connector and a female connector after one process.
FIG. 9 is a schematic view showing the connection state of the joint after the manual pretensioning is completed.
Fig. 10 is a schematic view showing the connection state of the screw thread after the manual pretensioning is completed.
Fig. 11 is a top view of the locking piece.
FIG. 12 is a stress distribution cloud chart of a variable tooth width thread of the duplex marine riser joint according to the present invention.
Fig. 13 is a stress distribution cloud of a conventional riser joint with equal thread width.
Wherein:
a male joint 100, a female joint 200, a male joint first thread 1, a female joint first thread 1 ', a male joint second thread 2, a female joint second thread 2 ', a locking block 3, a screw 4, a sealing ring 5, a groove 6, an annular groove 7, a female joint first bearing surface 8, a female joint first guide surface 9, a female joint second guide surface 9 ', a tooth bottom 10, the thread comprises a tooth crest 11, a main shoulder surface 12, a large end surface 13, a secondary shoulder surface 14, a small end surface 15, a female joint second equal-tooth-width thread 16, a male joint second variable-tooth-width thread 16 ', a female joint first equal-tooth-width thread 17, a male joint first variable-tooth-width thread 17 ', a female joint thread inflection point 18, a male joint thread inflection point 18 ', a female joint first variable-tooth-width thread 19, a male joint first equal-tooth-width thread 19 ', a female joint second variable-tooth-width thread 20 and a male joint second equal-tooth-width thread 20 '.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
Referring to fig. 1-13, the present invention relates to a two-line marine riser joint. I am named PT-CV with a specific model name. As shown in the figure: it is a two-line marine riser joint comprising a male joint 100 and a female joint 200 that are mated with each other.
Wherein:
the male connector 100 is provided with double-head external conical threads, the double-head external conical threads comprise male connector first threads 1 and male connector second threads 2 which are uniformly arranged at 180 degrees, and the male connector 100 is also provided with a small end face 15 and a main shoulder face 12;
the female connector 200 is provided with double-end inner tapered threads, the double-end inner tapered threads comprise female connector first threads 1 'and female connector second threads 2' which are uniformly arranged at 180 degrees, and the male connector 200 is further provided with a large end face 13 and an auxiliary shoulder face 14;
the male joint 100 and the female joint 200 are cooperatively connected by the male joint first thread 1, the male joint second thread 2, and the female joint first thread 1 'and the female joint second thread 2'.
The bearing angles of the bearing surfaces of the male connector 100 and the female connector 200 are negative bearing angles alpha, alpha ranges from-3 degrees to-5 degrees, the guide angle beta of the guide surface ranges from 40 degrees to 45 degrees, and the screw pitch is 12.7 mm; the tooth height is 3.0mm to 5.0mm, and the thread length of the external taper thread of the male joint 100 and the internal taper thread of the female joint 200 are both L.
Fig. 2 is a schematic view of the connection state of the thread teeth after the threading is finished, taking a female joint 200 as an example, on the same thread line, a female joint first bearing surface 8 and a female joint first guide surface 9 are connected through a tooth crest 11, a female joint groove is arranged between the female joint first bearing surface 8 and a female joint second guide surface 9' on the adjacent thread line, and the bottom of the female joint groove is a tooth bottom 10; the taper directions of the tooth crest 11 and the tooth bottom 10 are consistent with the taper direction of the female joint thread and are both 1: 16.365.
In the invention, the double-end external taper thread of the male connector 100 and the double-end internal taper thread of the female connector 200 are processed twice, after the processing is finished, the external taper thread of the male connector 100 comprises a male connector equal-tooth-width thread section and a male connector variable-tooth-width thread section, wherein the male connector equal-tooth-width thread section is close to the small end face, the male connector variable-tooth-width thread section is far away from the small end face, the length of the male connector equal-tooth-width thread section is 1/2L-3/5L, the thread tooth widths of the male connector equal-tooth-width thread section are unchanged, and the thread tooth widths of the male connector variable-tooth-width thread section are linearly reduced; correspondingly, the inner tapered thread of the female joint 200 comprises a female joint equal-tooth-width thread section and a female joint variable-tooth-width thread section, wherein the female joint equal-tooth-width thread section is close to the large end face, the female joint variable-tooth-width thread section is far away from the large end face, the length of the female joint equal-tooth-width thread section is 1/2L-3/5L, the tooth width of the female joint equal-tooth-width thread section is unchanged, and the tooth width of the female joint variable-tooth-width thread section is linearly reduced.
A male joint thread at the joint of the equal-tooth-width threaded section of the male joint and the variable-tooth-width threaded section of the male joint is called a male joint thread inflection point; that is, the inflection point of the thread of the male joint gradually and linearly decreases toward the tooth width of the thread of the male joint in one direction away from the small end surface;
a female joint thread at the joint of the equal-tooth-width threaded section of the female joint and the variable-tooth-width threaded section of the female joint is called a female joint thread inflection point; that is, the inflection point of the thread ridge of the box is gradually and linearly decreased toward the tooth width of the thread ridge of the box in one direction away from the large end surface;
the male joint threads marked in the drawing include a male joint thread inflection point 18 ', the male joint thread inflection point 18 ' is a first equal-tooth-width thread 19 ' and a second equal-tooth-width thread 20 ' of the male joint in sequence towards the direction of one side of the small end surface, and the male joint thread inflection point 18 ' is a first variable-tooth-width thread 17 ' and a second variable-tooth-width thread 16 ' of the male joint in sequence away from the direction of one side of the small end surface.
The female joint thread teeth marked in the drawing comprise a female joint thread tooth inflection point 18, the female joint thread tooth inflection point 18 towards the female joint thread tooth in the direction of the large end face side is a female joint first equal-tooth-width thread tooth 17 and a female joint second equal-tooth-width thread tooth 16 in sequence, and the female joint thread tooth in the direction of the female joint thread tooth inflection point 18 away from the large end face side is a female joint first variable-tooth-width thread tooth 19 and a female joint second variable-tooth-width thread tooth 20 in sequence.
Taking a female joint as an example, fig. 4 shows the female joint after the secondary machining is completed, OIP is a thread helix after the primary machining is completed, OIQ is a helix after the secondary machining, OIP is a straight line, and OIQ is divided into a line section OI and a line section IQ. The cutting thickness of the thread flank surface can be changed by changing the initial position and feed rate of the tool in the secondary working, as shown in fig. 5, and fig. 6 is a partially enlarged view of fig. 5. In the secondary processing, the cutter is not in contact with the second equal-tooth-width thread 16 of the female joint and the first equal-tooth-width thread 17 of the female joint, certain gaps exist between the second equal-tooth-width thread 16 of the female joint and the first equal-tooth-width thread 17 of the female joint and the bearing surface, and the gaps are a and b respectively, wherein a is larger than b; the tool is just in contact with the inflection point 18 of the thread tooth of the female joint, and no clearance or interference exists between the tool and the bearing surface, so that the tooth width of the thread tooth of the female joint, which is towards one side of the large end surface, of the inflection point 18 of the thread tooth of the female joint is not changed; interference occurs between the cutter and the first variable tooth width thread tooth 19 of the female joint and the second variable tooth width thread tooth 20 of the female joint, interference between the first variable tooth width thread tooth 19 of the female joint and the second variable tooth width thread tooth 20 of the female joint and the bearing surface are d and e respectively, wherein e is larger than d, and therefore the tooth width of the female joint in the direction of the inflection point 18 of the thread tooth of the female joint away from the large end surface is continuously reduced.
Fig. 7 shows the pin and the box after the secondary machining, in which the pitch of the thread is δ and the width of the tooth is u after the primary machining, see fig. 8. After secondary machining, the thread pitch of the thread is delta (delta is the axial distance between two corresponding points on the middle curve of adjacent threads on the guide surface), delta is 11-13 mm, the thread width mu of the female joint in the direction from the inflection point 18 of the threads of the female joint to one side of the large end surface is unchanged, the thread width mu of the female joint in the direction from the inflection point 18 of the threads of the female joint to one side of the large end surface is linearly reduced, the reduction amount between the adjacent threads is delta u, and delta u is 0.05-0.08 mm.
The thread of the male connector also needs to be processed twice, namely, once processing and twice processing, and is used together with the female connector, and in the screwing-in process, when the middle thread bearing surfaces start to contact, certain gaps exist between the thread bearing surfaces at two sides and gradually expand along the two sides, as shown in fig. 9, and fig. 10 is a partial enlarged view of fig. 9. When the bearing surfaces of the inflection point 18 of the female joint thread and the inflection point 18 'of the male joint thread are in contact, the clearance c' between the two is zero. A clearance a 'exists between the bearing surfaces of the second equal-tooth-width thread 16 of the female joint and the second variable-tooth-width thread 16' of the male joint, a clearance b 'exists between the bearing surfaces of the first equal-tooth-width thread 17 of the female joint and the first variable-tooth-width thread 17' of the male joint, a clearance d 'exists between the bearing surfaces of the first variable-tooth-width thread 19' of the female joint and the first variable-tooth-width thread 19 'of the male joint, a clearance e' exists between the bearing surfaces of the second variable-tooth-width thread 20 of the female joint and the second variable-tooth-width thread 20 'of the male joint, and the clearances a', b ', d' and e 'are larger towards two sides, namely, a' is larger than b ', d' is smaller than e; the advantages of the variable-tooth-width thread are explained by combining finite element analysis, fig. 12 is a stress distribution cloud chart of the variable-tooth-width thread when the interference magnitude of a main shoulder is 0.5mm, the contact force range borne by the thread is 1060 kN-1682 kN, the ratio of the maximum contact force to the minimum contact force borne by the thread is 1.59:1, fig. 13 is a thread stress distribution cloud chart with the same tooth width, the contact force range borne by the thread is 659 kN-2571 kN, the ratio of the maximum contact force to the minimum contact force borne by the thread is 3.9:1, and the contact force distribution of the variable-tooth-width thread is relatively uniform, so that the bearing capacity is higher. The darker the color in the stress distribution cloud represents the greater the stress.
The tooth tops of the outer cone threads and the tooth bottoms of the inner cone threads have certain gaps, the tooth bottoms of the outer cone threads and the tooth tops of the inner cone threads have certain gaps, when manual pre-tightening is finished, the gap f between the tooth tops and the tooth bottoms of the threads is 0.3-0.4 mm, and the number of turns of the manual pre-tightening can be improved to the greatest extent, and the number of turns of the machine tightening is reduced. The maximum tightening number of the joint can be finished by only 31/2 circles.
During the assembly process of the male connector and the female connector, the screwing-on is divided into manual pre-tightening and mechanical tightening, only guide surfaces are in contact at the time, when a middle thread bearing surface is in contact, the thread bearing surfaces at two sides are not in contact, the gap is gradually enlarged, the gap between the corresponding thread bearing surfaces begins to be reduced and contacted along with the increase of screwing-on turns, and the gap between the middle thread bearing surfaces is contacted along with the increase of screwing-on turns, and the gap between the bearing surfaces corresponding to the thread at two sides is gradually reduced and contacted along with the increase of screwing-on turns in the figure 7.
When the screwing-on is finished, the large end surface 13 of the female connector is contacted with the main shoulder surface 12 of the male connector, and the small end surface 15 of the male connector is contacted with the auxiliary shoulder surface 14 of the female connector.
The two sides of the main shoulder surface 12 are respectively provided with an annular groove 7 and two grooves 6 which are uniformly distributed, the grooves 6 are inwards arranged on the outer surface of the male connector, and the annular grooves 7 are inwards arranged on the inner edge of the main shoulder surface 12 of the male connector.
The annular groove 7 is used for placing the sealing ring 5, the groove 6 is used for placing the locking block 3, and the male connector 100 and the locking block 3 are connected through the screw 4. The locking piece 3 and the small end face 15 of the female connector are contacted with each other, on the contacted surfaces, the corresponding side surface of the locking piece 3 and the small end face 15 are provided with sawtooth belts, see fig. 11, and finally the male connector and the female connector are locked under the pressing force of the screw 4.
The above is only a specific application example of the present invention, and the protection scope of the present invention is not limited in any way. All the technical solutions formed by equivalent transformation or equivalent replacement fall within the protection scope of the present invention.
Claims (9)
1. A double-line marine riser joint comprises a male joint and a female joint which are matched with each other; the male connector is provided with a double-head external taper thread, and a small end face and a main shoulder face are also arranged on the male connector; the female joint is provided with double-end inner tapered threads, the male joint is also provided with a large end face and an auxiliary shoulder face, and the thread lengths of the outer tapered threads of the male joint and the inner tapered threads of the female joint are both L;
the method is characterized in that:
the external taper thread of the male joint comprises a male joint equal-tooth-width thread section and a male joint variable-tooth-width thread section, wherein the male joint equal-tooth-width thread section is close to the small end face, the male joint variable-tooth-width thread section is far away from the small end face, the length of the male joint equal-tooth-width thread section is 1/2L-3/5L, the tooth width of the thread of the male joint equal-tooth-width thread section is unchanged, and the tooth width of the thread of the male joint variable-tooth-width thread section is linearly reduced;
the inner cone thread of the female joint comprises a female joint equal-tooth-width thread section and a female joint variable-tooth-width thread section, wherein the female joint equal-tooth-width thread section is close to the large end face, the female joint variable-tooth-width thread section is far away from the large end face, the length of the female joint equal-tooth-width thread section is 1/2L-3/5L, the tooth width of the female joint equal-tooth-width thread section is unchanged, and the tooth width of the female joint variable-tooth-width thread section is linearly reduced.
2. The marine riser joint according to claim 1, wherein there is a gap between the crests of the male and female threads and a gap between the roots of the male and female threads.
3. The two-wire marine riser joint according to claim 2, wherein the clearance f is 0.3-0.4 mm.
4. The double-line marine riser joint according to claim 1, wherein the bearing surface of the male and female joints has a negative bearing angle α, α is-3 to-5 °, the guide surface has a guide angle β of 40 to 45 °, and the thread pitch is 12.7 mm; the tooth height is 3.0 mm-5.0 mm.
5. The marine riser joint of claim 1, wherein on the same thread line, the first bearing surface of the box and the first guide surface of the box are connected by a crest, and a box recess is formed between the first bearing surface of the box and the second guide surface of the box on the adjacent thread line, and the bottom of the box recess is a root; the taper directions of the tooth top and the tooth bottom are consistent with the taper direction of the female joint thread and are both 1: 16.365.
6. The duplex marine riser joint according to claim 1, wherein the linear decrease in thread tooth width of the male joint variable tooth width threaded section and the linear decrease in thread tooth width of the female joint variable tooth width threaded section decrease by an amount Δ u, Δ u being 0.05-0.08 mm.
7. The marine riser joint of claim 1, wherein during assembly of the pin and box, when the intermediate thread bearing surfaces are in contact, the two side thread bearing surfaces are not in contact and the gap gradually increases, and as the number of make-up turns increases, the gap between the corresponding thread bearing surfaces begins to decrease and contact.
8. The double-line marine riser joint according to claim 1, wherein the main shoulder surface has an annular groove and two evenly distributed grooves on both sides, the grooves are formed inward from the outer surface of the male joint, the annular groove is formed inward from the inner edge of the main shoulder surface of the male joint, the annular groove is provided with a seal ring therein, the grooves are provided with locking pieces, the male joint and the locking pieces are connected by screws, and the locking pieces are in contact with the small end surfaces of the female joint.
9. The marine riser joint of claim 8, wherein the surfaces of the locking piece that contact the small end surface of the female joint have cooperating serrated strips.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910814009.9A CN110608321A (en) | 2019-08-30 | 2019-08-30 | Double-line marine riser joint |
| PCT/CN2020/082890 WO2021036261A1 (en) | 2019-08-30 | 2020-04-02 | Double-line marine riser coupling |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910814009.9A CN110608321A (en) | 2019-08-30 | 2019-08-30 | Double-line marine riser joint |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN110608321A true CN110608321A (en) | 2019-12-24 |
Family
ID=68890715
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910814009.9A Pending CN110608321A (en) | 2019-08-30 | 2019-08-30 | Double-line marine riser joint |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN110608321A (en) |
| WO (1) | WO2021036261A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2021036261A1 (en) * | 2019-08-30 | 2021-03-04 | 江苏璞腾油气装备有限公司 | Double-line marine riser coupling |
Citations (5)
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| CN105793630A (en) * | 2013-12-05 | 2016-07-20 | 新日铁住金株式会社 | Threaded joint for steel pipes |
| CN108138994A (en) * | 2015-10-21 | 2018-06-08 | 新日铁住金株式会社 | Screw joint for steel pipe |
| CN210920416U (en) * | 2019-08-30 | 2020-07-03 | 江苏璞腾油气装备有限公司 | Double-line marine riser joint |
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| RU2440481C1 (en) * | 2010-06-15 | 2012-01-20 | Юрий Константинович Низиенко | Tight threaded connection of pipes in process string of geological exploration drilling device |
| KR101616353B1 (en) * | 2014-12-26 | 2016-04-28 | 주식회사 포스코 | Joint structure for connecting pipe |
| CN106761462B (en) * | 2016-12-27 | 2019-01-18 | 中国石油天然气集团公司 | A kind of oil well casing special nipple |
| CN208189877U (en) * | 2018-02-22 | 2018-12-04 | 苏州贝尔特光伏电子科技有限公司 | A kind of photovoltaic panel waterproof connector |
| CN110608321A (en) * | 2019-08-30 | 2019-12-24 | 江苏璞腾油气装备有限公司 | Double-line marine riser joint |
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2019
- 2019-08-30 CN CN201910814009.9A patent/CN110608321A/en active Pending
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2020
- 2020-04-02 WO PCT/CN2020/082890 patent/WO2021036261A1/en active Application Filing
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| CN201198739Y (en) * | 2008-03-28 | 2009-02-25 | 上海海隆石油管材研究所 | Petroleum drill rod joint with higher anti-twisting strength |
| CN103291228A (en) * | 2013-06-07 | 2013-09-11 | 中国石油集团石油管工程技术研究院 | Oil casing special threads and machining method thereof |
| CN105793630A (en) * | 2013-12-05 | 2016-07-20 | 新日铁住金株式会社 | Threaded joint for steel pipes |
| CN108138994A (en) * | 2015-10-21 | 2018-06-08 | 新日铁住金株式会社 | Screw joint for steel pipe |
| CN210920416U (en) * | 2019-08-30 | 2020-07-03 | 江苏璞腾油气装备有限公司 | Double-line marine riser joint |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| WO2021036261A1 (en) * | 2019-08-30 | 2021-03-04 | 江苏璞腾油气装备有限公司 | Double-line marine riser coupling |
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| WO2021036261A1 (en) | 2021-03-04 |
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