NL2023800B1 - Threaded connection for exploration and production of a hydrocarbon well - Google Patents

Threaded connection for exploration and production of a hydrocarbon well Download PDF

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Publication number
NL2023800B1
NL2023800B1 NL2023800A NL2023800A NL2023800B1 NL 2023800 B1 NL2023800 B1 NL 2023800B1 NL 2023800 A NL2023800 A NL 2023800A NL 2023800 A NL2023800 A NL 2023800A NL 2023800 B1 NL2023800 B1 NL 2023800B1
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NL
Netherlands
Prior art keywords
threaded connection
threads
rim
inch
box
Prior art date
Application number
NL2023800A
Other languages
Dutch (nl)
Inventor
Mutis Rueda David
Alberto Cordero Jorge
Original Assignee
Hydril Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Application filed by Hydril Co filed Critical Hydril Co
Priority to NL2023800A priority Critical patent/NL2023800B1/en
Priority to CN202080050120.6A priority patent/CN114080486A/en
Priority to EP20746524.6A priority patent/EP3997300A1/en
Priority to MX2022000513A priority patent/MX2022000513A/en
Priority to PCT/US2020/041757 priority patent/WO2021011443A1/en
Priority to BR112022000485A priority patent/BR112022000485A2/en
Priority to US17/626,396 priority patent/US20220290784A1/en
Priority to CA3144973A priority patent/CA3144973A1/en
Application granted granted Critical
Publication of NL2023800B1 publication Critical patent/NL2023800B1/en
Priority to CONC2022/0000056A priority patent/CO2022000056A2/en

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B17/00—Drilling rods or pipes; Flexible drill strings; Kellies; Drill collars; Sucker rods; Cables; Casings; Tubings
    • E21B17/02—Couplings; joints
    • E21B17/04—Couplings; joints between rod or the like and bit or between rod and rod or the like
    • E21B17/042—Threaded

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  • Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Mining & Mineral Resources (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Fluid Mechanics (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Non-Disconnectible Joints And Screw-Threaded Joints (AREA)
  • Earth Drilling (AREA)

Abstract

A threaded connection for exploration and production of a hydrocarbon well and comprising a coupling member, a first tubular member and a second tubular member, wherein the coupling 5 member has a coupling outer diameter, a first box part with first inner threads, and a second box part with second inner threads, the first tubular member has a first unthreaded tube part, and a first pin part with first outer threads, the second tubular member has a second unthreaded tube part, and a second pin part with second outer threads, the first inner threads and the first outer threads are configured to form a first inner primary seal at final make-up, 10 and the second inner threads and the second outer threads are configured to form a second inner primary seal at final make-up.

Description

Title: Threaded connection for exploration and production of a hydrocarbon well
FIELD OF THE INVENTION The invention relates to a threaded connection for exploration and production of a hydrocarbon well and comprising a coupling member, a first tubular member and a second tubular member. Such a threaded connection comprising a coupling member for coupling the first and second tubular members end-to-end is also referred to as a “threaded and coupled” connection.
In the known threaded connection, the coupling member has a coupling outer diameter COD, a first box part with first inner threads, and a second box part with second inner threads. The first box part and the second box part have a radial box part thickness A located between the first inner threads and the second inner threads. The first tubular member has a first unthreaded tube part, and a first pin part with first outer threads. The second tubular member has a second unthreaded tube part, and a second pin part with second outer threads. The first unthreaded tube part and the second unthreaded tube part have a tube outer diameter TOD and a radial tube wall thickness W. The coupling outer diameter COD is larger than the tube outer diameter TOD. The first inner threads, the second inner threads, the first outer threads, and the second outer threads have dovetail wedge threads. The first inner threads and the first outer threads are configured to form a first inner primary seal at final make-up. The second inner threads and the second outer threads are configured to form a second inner primary seal at final make-up.
The first and second inner primary seals form at final make-up the first line of defense against internal pressure in the threaded connection.
BACKGROUND OF THE INVENTION In some situations, the known threaded connection has too large an outside diameter for use in exploration and/or production of specific smaller diameter hydrocarbon wells, such as so- called slender profiled hydrocarbon wells sometimes referred to as slim-hole wellbores or slim-hole completions.
SUMMARY OF THE INVENTION The invention has the objective to provide an improved, or at least alternative, threaded connection, which can be used in said specific smaller diameter hydrocarbon wells.
2. This objective is reached by a threaded connection for exploration and production of a hydrocarbon well and comprising; - a coupling member having a coupling outer diameter COD and comprising a first box part comprising first inner threads, a second box part comprising second inner threads, and a rim part comprising a radially extending inner rim, wherein the rim part is located between the first box part and the second box part and has a radial rim part thickness B and an axial rim part length C, and the first box part and the second box part have a radial box part thickness A between the inner rim and, respectively, the first inner threads and the second inner threads, - a first tubular member comprising a first unthreaded tube part, and a first pin part comprising first outer threads, and - a second tubular member comprising a second unthreaded tube part, and a second pin part comprising second outer threads, wherein -- the first unthreaded tube part and the second unthreaded tube part have a tube outer diameter TOD and a radial tube wall thickness W, -- the first tubular member and the second tubular member have a tube inner diameter TID, -- the first inner threads, the second inner threads, the first outer threads, and the second outer threads have dovetail wedge threads, -- the first inner threads and the first outer threads are configured to form a first inner primary seal at final make-up, -- the second inner threads and the second outer threads are configured to form a second inner primary seal at final make-up, and -- the threaded connection complies to; COD > TOD B = about ((COD — TID) / 2) C>O, and A<W.
COD > TOD indicates that the coupling outer diameter COD of the coupling member is larger than the tube outer diameter TOD of the first unthreaded tube part of the first tubular member and the second unthreaded tube part of the second tubular member. When compared with the known threaded connection, the rim part has been added between the first box part and the second box part. The rim part thickness B of the rim part is
-3- measured in radial direction with respect to a longitudinal axis of the threaded connection and the rim part length C is measured in axial direction.
B = (COD — TID) / 2 indicates that the rim part extends from the coupling outer diameter COD of the coupling member up to the tube inner diameter TID of the first tube member and the second tube member. This facilitates the flowing of fluid through the threaded connection.
That B is “about” the value of (COD — TID) / 2 is to express that B may differ from the value of (COD —TID)/ 2 to an extent that the difference does not interfere with the function of the rim and the functioning of the connection. The difference may for instance be the result of machine tolerances.
C > O indicates that that the rim part with an axial rim part length C has been added to the threaded connection.
A threaded connection according to the invention comprising a coupling member for coupling a first and a second tubular member end-to-end is also referred to as a “threaded and coupled” connection.
The functioning of the first and second inner primary seals can be impaired when the internal pressures of fluids flowing through the threaded connection are too high and separate the first inner threads from the first outer threads and the second inner threads from the second outer threads.
In order to withstand these high internal pressures, the coupling member of the known threaded connection has a relatively large radial box part thickness A measured between the first inner threads and the second inner threads of the coupling member. In the known threaded connection, the radial box part thickness A is larger than the radial tube wall thickness W of the first unthreaded tube part of the first tubular member and the second unthreaded tube part of the second tubular member. This results in a relatively large coupling outer diameter.
The separation of the first inner threads from the first outer threads and the second inner threads from the second outer threads is caused by the radial deformation created by the internal pressures of the fluids flowing through the threaded connection. The invention is based on the insight that said radial deformation is associated with the hoop stresses in the threaded connection and that these hoop stresses can be reduced by addition of the rim part of the threaded connection according to the invention.
-4- This means that by adding the rim part to the known threaded connection, the radial box part thickness A of the coupling member can be reduced while ensuring that the first inner primary seal between the first inner threads and the first outer threads and the second inner primary seal between the second inner thread and the second outer threads is maintained. As a result, the radial box part thickness A of the first and second box parts of the coupling member of the threaded connection according to the invention is smaller than the radial tube wall thickness W of the first and second unthreaded tube parts of the first and second tubular members. This is indicated by A < W.
The reduced radial box part thickness A can be achieved by removing material at the outer coupling surface of the coupling member while keeping the first and second inner threads of the coupling member and the tubular members unchanged. This way, the coupling outer diameter COD is reduced and the threaded connection can be used in said specific smaller hydrocarbon wells, even if standardised tubular members are used.
In an embodiment of the threaded connection, the axial rim part length C of the rim part complies to; C < 31,75 mm (1.25 inch), preferably C < 27,94 mm (1.1 inch), more preferably C s 25,4 mm (1.0 inch).
In an embodiment of the threaded connection, the axial rim part length C of the rim part complies to; C 2 6,35 mm (0.25 inch), preferably C = 10,16 mm (0.4 inch), more preferably C = 12,7 mm {0.5 inch).
In an embodiment of the threaded connection, the axial rim part length C of the rim part complies to; 20,32 mm (0.8 inch) < C < 27,94 mm (1.1 inch), preferably C = 25,4 mm (1.0 inch) In an embodiment of the threaded connection, the threaded connection complies to; A < 0,9W, preferably A < 0,8W. This indicates that the radial box part thickness A is smaller than or equal to 90%, preferably 80%, of the radial tube wall thickness W.
In an embodiment of the threaded connection, the threaded connection complies to; A 2 0,7W. This indicates that the radial box part thickness A is larger than or equal to 70% of the radial tube wall thickness W.
In an embodiment of the threaded connection, the radial box part thickness A located is at the critical cross section of the first box part and the second box part.
-5- In an embodiment of the threaded connection, the tube outer diameter TOD of the first and second unthreaded tube parts of the first and second tubular members complies to; 114,3 mm (4.5 inch) < TOD < 244,5 mm (9 5/8 inch), preferably 114,3 mm (4.5 inch) < TOD < 193.7 mm (7.625 inch), more preferably 114,3 mm (4.5 inch) < TOD s 139,7 mm (5.5 inch).
In an embodiment of the threaded connection, the radial tube wall thickness W of the first and second unthreaded tube parts of the first and second tubular members complies to: 6.3 mm (0.250 inch) = W = 12.7 mm (0.500 inch), preferably 7.3 mm (0.290 inch) = W s 11.1 mm (0.437 inch).
In an embodiment of the threaded connection, the threaded connection comprises the features that in a first direction from the inner rim and towards the first inner primary seal, the first inner threads and the first outer threads start to have full contact at a first seal starting position, in an opposite second direction from the inner rim and towards the second inner primary seal, the second inner threads and the second outer threads start to have full contact at a second seal starting position, the first seal starting position is located at an axial seal distance D from the second seal starting position, and D > C.
In an embodiment of the threaded connection, the threaded connection complies to:
3.6mm (0.142 inch) = (D-C)/2 = 9.9 mm (0.392 inch). This indicates that the first and second seal starting positions are located at an axial distance from the rim part of more than or equal to 3.6 mm (0.142 inch) and less than or equal to 9.9 mm (0.392 inch). Preferably, the threaded connection complies to: 5 mm (0.2 inch) <(D -C)/2 <7.7 mm (0.3 inch), more preferably (D-C) / 2 is 6.1 mm (0.242 inch).
In an embodiment of the threaded connection, the radially extending inner rim is located between the first pin part and the second pin part.
In an embodiment of the threaded connection, the first tubular member comprises a first pin nose, the second tubular member comprises a second pin nose, and at final make-up the first pine nose and the second pin nose are located at a distance from the inner rim.
In an embodiment of the threaded connection, the radially extending inner rim is located between the first pin nose and the second pin nose.
In an embodiment of the threaded connection, the threaded connection is at final make-up free from any further inner seal {in addition to the first inner primary seal and the second inner primary seal). In an embodiment of the threaded connection, the threaded connection is at
-6- final make-up free from any further secondary seal or metal-to-metal seal (in addition to the first inner primary seal and the second inner primary seal and the engagement of the complete threads).
In an embodiment of the threaded connection, the first inner threads and the first outer threads together form a first thread step, and the second inner threads and the second outer threads together form a second thread step.
In an embodiment of the threaded connection, the threaded connection is free from any further thread step (in addition to the first thread step and the second thread step). The first thread step and the second thread step are both single thread steps. In an embodiment of the threaded connection, the first thread step and the second thread steps are tapered thread steps.
In an embodiment of the threaded connection, the coupling member comprises a first relief groove located between the first inner threads and the inner rim and a second relief groove located between the second inner threads and the inner rim. The first and second relief grooves are during the production process of the coupling member used by the lathe tools to move away from the first and second inner threads and out of the coupling member without damaging the radially extending inner rim after the first and second inner threads are formed. In an embodiment of the threaded connection, the coupling outer diameter COD is the largest diametric dimension of the threaded connection.
In an embodiment of the threaded connection, the rim part has a rim inner diameter RID and the threaded connection complies to; RID = about TID. This indicates that the rim part, more specifically the inner rim, is flush or near flush with the first and second tubular members. That the RID is about the value of TID is to express that RID may differ from TID to an extent that the difference does not interfere with the function of the rim and the functioning of the connection. The difference between TID and RID may for instance be the result of machine tolerances. In a preferred embodiment RID = TID + 0.127 mm (0.050 inch). In a more preferred embodiment RID = TID.
In an embodiment of the threaded connection, the rim part has a rim outer diameter ROD and the threaded connection complies to: B = (ROD — RID)/2. This indicates that the radial rim part thickness B extends from the rim outer diameter ROD up to the rim inner diameter RID.
-7- In an embodiment of the threaded connection, the threaded connection complies to; COD = ROD. This indicates that the coupling outer diameter COD and the rim outer diameter ROD are equal to each other.
In an embodiment of the threaded connection, the first box part has a first box outer diameter FBOD, the second box part has a second box outer diameter SBOD, and the threaded connection complies to; COD = FBOD = SBOD. This indicates that the coupling outer diameter COD, the first box outer diameter FBOD, and the second box outer diameter SBOD are equal to each other.
In an embodiment of the threaded connection, the threaded connection defines a longitudinal axis.
In an embodiment of the threaded connection, the rim part and the inner rim completely surround the longitudinal axis.
In an embodiment of the threaded connection, the rim part comprises a rim inner surface which is near flush, preferably flush, with a first tube inner surface of the first tubular member and a second tube inner surface of the second tubular member.
BRIEF DESCRIPTION OF THE INVENTION Embodiments of the threaded connection according to the invention will be described by way of example only, wherein reference to the accompanying schematic drawings in which corresponding reference symbols indicate corresponding parts, and in which: Figure 1A schematically shows a view in perspective of an embodiment of the threaded connection according to the invention, Figure 1B schematically shows a cross sectional view of the threaded connection of figure 1, Figure 2 schematically shows an enlarged view of part II of figure 1. Figure 3 schematically shows an enlarged view of part II! of figure 2.
Figure 4 contains graph 1 showing the hoop stresses in different embodiments of a threaded connection (b-n} having the construction of figure 1 and in a threaded connection (a) without rim part, Figure 5 contains graph 2 showing the hoop stresses at the first seal starting position of the threaded connections (a-n) of graph 1, and Figure 6 contains graph 3 showing the hoop stresses at the first seal starting position of alternative embodiments a’-n’ of the threaded connections of graph 2.
-8-
DETAILED DESCRIPTION OF THE INVENTION Figure 1 shows a view in perspective of an embodiment of the threaded connection 1 according to the invention at final make-up 20. The threaded connection 1 for exploration and production of a hydrocarbon well comprises a coupling member 2, a first tubular member 9 and a second tubular member 13. Parts of the coupling member 2, the first tubular member 9 and the second tubular member 13 are cut out to show more details of the threaded connection 1. Figure 2 shows an enlarged view of part II of figure 1. Figure 3 shows an enlarged view of part III of figure 2.
The threaded connection 1 defines a longitudinal axis 31. The coupling member 2 has a coupling outer diameter COD defined by an outer coupling surface 35, a first box part 3 comprising first inner threads 4, a second box part 5 comprising second inner threads 6, and a rim part 7 comprising a radially extending inner rim 8. The first box part 3 has a first box length FBL. The second box part 5 has a second box length SBL. The rim part 7 is located between the first box part 3 and the second box part 5 and has a radial rim part thickness B and an axial rim part length C. The first box part 3 and the second box part 5 have a radial box part thickness A between, respectively, the inner rim 8 and the first inner threads 4 and the second inner threads 6.
The first tubular member 9 comprises a first unthreaded tube part 10, and a first pin part 11 comprising first outer threads 12.
The second tubular member 13 comprises a second unthreaded tube part 14, and a second pin part 15 comprising second outer threads 16.
The first unthreaded tube part 10 and the second unthreaded tube part 14 have a tube outer diameter TOD and a radial tube wall thickness W.
The first tubular member 9 and the second tubular member 13 have a tube inner diameter TID.
The first inner threads 4, the second inner threads 6, the first outer threads 12, and the second outer threads 16 have dovetail wedge threads 17.
Dovetail wedge threads 17 are characterised by threads having a negative flank angle for their stab flanks and load flanks. The dovetail wedge threads 17 increase in width in opposite directions on the pin part and the corresponding box part. The rate at which the dovetail
-9- wedge threads 17 change in width is defined by a variable commonly known as a “wedge ratio”. Wedge ratio (although technically not a ratio) refers to the difference between the stab flank lead and the load flank lead, which causes the dovetail wedge threads 17 to vary in width along the threaded connection. A “lead” of a thread refers to the differential distance between a component of a thread on consecutive threads. As such, the "stab flank lead" is the distance between stab flanks of consecutive thread pitches along the axial length of the threaded tubular connection. The first inner threads 4 and the first outer threads 12 are configured to form a first inner primary seal 19 at final make-up 20. The second inner threads 6 and the second outer threads 16 are configured to form a second inner primary seal 18 at final make-up 20.
The term "make-up" refers to engaging the first and second pin parts 11, 15 into the first and second box parts 3, 5 and threading said parts together by applying a torque. The final make-up 20 refers to the situation that the make-up has been completed by threading the first and second pin parts 11, 15 and the first and second box parts 3, 5 together up to a desired amount of torque, or up to the first and second pin parts 11, 15 reach a specific position relative to the first and second box parts 3, 5.
The first inner primary seal 19 is formed by full contact between the first inner threads 4 and the first outer threads 12, and the second inner primary seal 18 is formed by full contact between the second inner threads 6 and the second outer threads 16.
The first and second inner primary seals 18, 19 form at final make-up 20 the first line of defence against internal pressure in the threaded connection 1.
The threaded connection 1 complies to; COD > TOD B = (COD -TID)/2 C=>0, and A<W. COD > TOD indicates that the coupling outer diameter COD of the coupling member 2 is larger than the tube outer diameter TOD of the first unthreaded tube part 10 and the second unthreaded tube part 14.
-10 - When compared with the known threaded connection, the rim part 7 has been added between the first box part 3 and the second box part 5. The rim part 7 has the same outer dimensions as the first and second box parts 3, 5 and has an inner rim 8 extending internally in a radial direction towards the longitudinal axis 31 and located between the first pin part 11 of first tubular member 9 and the second pin part 15 of the second tubular member 13. The rim part 7 surrounds the longitudinal axis 31 completely and has a rim part thickness B measured in radial direction and a rim part length C measured in axial direction. The inner rim 8 is a circumferential rim surrounding the longitudinal axis 31. B=(COD -TID)/ 2 indicates that the inner rim 8 extends from the coupling outer diameter COD of the coupling member up to the tube inner diameter TID. This facilitates the flowing of fluid through the threaded connection 1. The rim part 7 comprises a rim inner surface 34 which is flush with a first tube inner surface 32 of the first tubular member 9 and a second tube inner surface 33 of the second tubular member 13. C > O indicates that the rim part 7 with an axial rim part length C has been added to the threaded connection.
The axial rim part length C may comply to; C s 31,75 mm (1.25 inch), preferably C < 27,94 mm (1.1 inch), more preferably C < 25,4 mm (1.0 inch). The axial rim part length C may comply to; C = 6,35 mm (0.25 inch), preferably C = 10,16 mm (0.4 inch), more preferably C 2 12,7 mm (0.5 inch). The axial rim part length C may comply to; 20,32 mm (0.8 inch) < C s 27,94 mm (1.1 inch), preferably C = 25,4 mm (1.0 inch). A <Wa indicates that the radial box part thickness A of the first and second box parts 3, 5 is smaller than the radial tube wall thickness W of the first and second unthreaded tube parts 10, 14 of the first and second tubular members 9, 13. In order to withstand high internal pressures, the known threaded connections 1 typically have a radial box part thickness A which is larger than the radial tube part thickness W. This results in a large coupling outer diameter COD.
-11- The rim part 7 of the threaded connection 1 according to the invention allows that the radial box part thickness A can be reduced while ensuring that the first and second inner primary seals 18, 19 are maintained when subjected to the high internal pressures. As a result, the threaded connection 1 with a smaller coupling outer diameter COD can be provided due to which the threaded connection 1 can be used in smaller diameter hydrocarbon wells, such as so-called slender profiled hydrocarbon wells sometimes referred to as slim-hole wellbores or slim-hole completions. The largest diametric dimension of this type of threaded connection 1 is typically formed by the coupling outer diameter COD of the coupling member 2. For this type of threaded connection 1 for exploration and production of a hydrocarbon well, tubular members with a standardised tube outer diameter TOD are in typically used for the first and second tubular members 9, 13. To reduce the largest diametric dimension of the threaded connection 1 it is required to reduce the radial box part thickness A of the coupling member 2.
The radial box part thickness A and the radial tube wall thickness W may comply to; A < 0,9W, preferably A <0,8W. The radial box part thickness A and the radial tube wall thickness W may comply to; A = 0,7W. The radial box part thickness A is located at the critical cross section of the first box part 3 and the second box part 5.
The tube outer diameter TOD may comply to: 114,3 mm (4.5 inch) < TOD < 244,5 mm (9 5/8 inch), preferably 114,3 mm (4.5 inch) < TOD =< 193.7 mm (7.625 inch), more preferably 114,3 mm (4.5 inch) < TOD s 139,7 mm (5.5 inch).
The radial tube wall thickness W may comply to: 6.3 mm {0.250 inch) = Ws 12.7 mm (0.500 inch), preferably 7.3 mm {0.290 inch) s Ws 11.1 mm (0.437 inch). In a first direction 21 from the inner rim 8 and towards the first inner primary seal 19, the first inner threads 4 and the first outer threads 12 start to have full contact at a first seal starting position 22. In an opposite second direction 23 from the inner rim 8 and towards the second inner primary seal 18, the second inner threads 6 and the second outer threads 16 start to have full contact at a second seal starting position 24. The first seal starting position 22 is
-12- located at an axial seal distance D from the second seal starting position 24. The axial seal distance D is larger than the axial rim part length C. In other words, the axial seal distance D and the axial rim part length C comply to: D > C.
The axial rim part length C and the axial seal distance D may comply to: 3.6 mm (0.142 inch) sS(D-C)/259.9 mm (0.392 inch), preferably 5 mm (0.2 inchy<(D-C)/2<7.7 mm (0.3 inch), more preferably (D-C) / 2 is 6.1 mm (0.242 inch).
The radially extending inner rim 8 is located between the first pin part 11 and the second pin part 15. The first tubular member 9 comprises a first pin nose 25, the second tubular member 13 comprises a second pin nose 26, and at final make-up 20 the first pin nose 25 and the second pin nose 26 are located at a distance from the inner rim 8 (see figure 3).
The radially extending inner rim 8 is located between the first pin nose 26 and the second pin nose 26. At final make-up 20, the threaded connection 1 is free from any further inner seal in addition to the first inner primary seal 19 and the second inner primary seal 18. The first inner threads 4 and the first outer threads 12 together form a first thread step 27. The second inner threads 6 and the second outer threads 16 together form a second thread step 28. The threaded connection 1 is free from any further thread step. This means that there are no further thread steps in addition to the first thread step 27 and the second thread step 28. The first thread step 27 and the second thread step 28 are tapered thread steps. The coupling member 2 comprises a first relief groove 29 located between the first inner threads 4 and the inner rim 8 and a second relief groove 30 located between the second inner threads 6 and the inner rim 8. In the shown embodiment, the rim part 7 has a rim inner diameter RID which is equal to the tube inner diameter TID. In other words, the tube inner diameter TID and the rim inner diameter RID comply to; TID = RID. In other embodiments there may be a difference tube inner diameter TID and the rim inner diameter RID, for instance in the order of + 0.127 mm (0.050 inch).
-13- The rim part 7 has a rim outer diameter ROD and radial rim part thickness B is equal to the difference between the rim outer diameter ROD and the rim inner diameter RID divided by two. In other words, the radial rim part thickness B, the rim outer diameter ROD, and the rim inner diameter RID comply to; B = (ROD — RID)/2.
The coupling outer diameter COD is equal to the rim outer diameter ROD. In other words, the coupling outer diameter COD and the rim outer diameter ROD comply to; COD = ROD. The first box part 3 has a first box outer diameter FBOD, the second box part 5 has a second box outer diameter SBOD, which both are equal to the coupling outer diameter COD. In other words, the coupling outer diameter COD, the first box outer diameter FBOD, and the second box outer diameter SBOD comply to; COD = FBOD = SBOD. Figure 4 contains graph 1 showing the hoop stresses in different embodiments of a threaded connection (b-n) having the construction of figure 1 and in a threaded connection (a) without rim part 7. For all the threaded connections a-n, the tube outer diameter TOD is 139,7 mm (5.5 inch), the tube inner diameter TID is 121.3 mm (4.776 inch), the radial tube wall thickness Wis 9.2 mm (0.361 inch), the coupling outer diameter COD is 148,6 mm (5.852 inch), and the radial box part thickness A is 6,9 mm (0,271 inch). Graph 1 shows the hoop stresses in the threaded connections a-n over their normalised length for an internal pressure of 555 Bar (8050 PSI). The length of the threaded connections a-nis normalised from 0 to 1. The length of the normalization involves the distance between the distal end of the complete formed first threads and the distal end of the complete formed first threads. The end of the complete formed threads is where the complete formed threads pass into incomplete threads. The proximal end of the complete formed threads is the end closed to the rim, whereas the distal end of the complete formed threads is the end furthest away from the rim. The vertical lines a-n indicate the respective first and second seal starting positions 22, 24 of the threaded connections a-n. The threaded connection a is not part of the invention because it does not have a rim part 7 comprising a radially extending inner rim 8.
-14 - The threaded connections b-n have the same construction as the threaded connection a with the difference that a rim part 7 comprising a radially extending inner rim 8 has been added between first and second box parts 3, 5. The threaded connections b-n differ from each other in that they have a different axial rim part length C. The axial rim part length C of the threaded connections b-n is indicated in table 1. All the threaded connections b-n have a radial rim part thickness B of 13.64 mm (0.537 inch). FL [ewww [were FT Pee [ese FT [wweemew [wessemmem [ewe wwe ee emery ee [wove TC [eee werewee Table 1 The different positions of the first and second seal starting positions 22, 24 indicated in graph 1 by the vertical lines a-n are caused by the different axial rim part length C of the rim parts 7 of the threaded connections b-n.
The rim parts 7 of the threaded connections b-n are added between the first and second box parts 3, 5 of the threaded connection a. Compared with the threaded connection a, the length of the threaded connections b-n is increased (in axial direction} with an amount equal to their axial rim part length C.
Figure 5 contains graph 2 showing the hoop stresses at the first seal starting position 22 of the threaded connections (a-n) of figure 4. Said hoop stresses are also indicate in table 1.
-15- Graph 1 indicates that the hoop stresses at the second seal starting positions 24 are the same as at the first seal starting positions 22. If the radial deformation (and the associates hoop stress) at the first and second seal starting positions 22, 24 are too high, the first and second inner primary seals 18, 19 will be impaired due to the separation of the first inner threads 4 from the first outer threads 12 the first seal starting position 22 and of the second inner threads 6 from the second outer threads 16 at the second seal starting position 24. Once separation at the first and second seal starting positions 22, 24 occurs due to the radial deformation caused by the internal pressure, the remainder of the first inner threads 4 will be separated easier from the remainder of the first outer threads 12 and the remainder of the second inner threads 6 will be separated easier from the rest of the second outer threads 16. Comparing the threaded connection a (without rim part 7) with the threaded connections b-n (with rim part 7) in the graphs 1 and 2 reveals that the rim parts 7 reduce the hoop stresses in threaded connections b-n. Especially the degree of hoop stresses at the first and second seal starting position 22, 24 are relevant, because too high hoop stresses (and associated radial deformations) at said first and second seal starting position 22, 24 will impair the first and second inner primary seals 18, 19. Beyond the first and second seal starting positions 22, 24, the hoop stresses (and associated radial deformations) are much less relevant, because the internal pressure does not go beyond the first and second seal starting positions 22, 24 when the first and second inner primary seals 18, 19 are maintained.
The graphs 1 and 2 also reveal that the dimension of the axial rim part length C has an effect on the degree of reduction of the hoop stresses in the threaded connections b-n, and in particular at their first and second seal starting positions 22, 24. At first the reduction of hoop stresses at the first and second seal starting positions 22, 24 increases when the axial rim part length C increases, but said further reduction fades away when the axial rim part length C is further increased. A too large axial rim part length C has the disadvantage that the total length of the coupling member 2 (sum of the first box length FBL of the first box part 3, the rim part length C of the rim part 7, and the second box length SBL of the second box part 5) increases without having additional benefit in terms of reduction of the hoop stresses at the first and second seal starting position 22, 24. Furthermore, adding more to the total length of the coupling will
- 16 - increase the cost in material. Still further, when exceeding a certain total length, may limit the use of certain field equipment for making-up the connection. A too small axial rim part length C has the disadvantage that the inner rim 8 can be damaged easily.
Figure 6 contains graph 3 showing the hoop stresses at the first seal starting position 22 of alternative embodiments a’-n’ of the threaded connections a-n of graph 2. For all the threaded connections a’-n’, the tube outer diameter TOD is 114,3 mm (4.5 inch), the tube inner diameter TID is 99,6 mm (3.920 inch), the radial tube wall thickness W is 7.4 mm (0.290 inch), the coupling outer diameter COD is 122 mm (4.803 inch), and the radial box part thickness A is 5.4 mm (0.213 inch). Again, the threaded connection a’ is not part of the invention because it does not have a rim part 7 comprising a radially extending inner rim 8.
Again, the threaded connections b’-n’ differ from each other in that they have a different axial rim part length C. The axial rim part length C of the threaded connections b’-n’ is indicated in table 2. All the threaded connections b’-n’ have a radial rim part thickness B of 11.2 mm (0.442 inch).
The hoop stresses at the first seal starting position 22 of the threaded connections a’-n’ for an internal pressure of 555 Bar (8050 PSI) are also indicated in table 2. The hoop stresses at the second seal starting positions 24 are the same as at the first seal starting positions 22.
FT [mewn [ews FT [eewenew [emeewe [ees [wre Freese ewes Ce wesw ee eeen
-17 - Teese ern [een [ewes Table 2 The same effects as described in relation to the graphs 1 and 2 of the threaded connections a-n are revealed in graph 3 of the threaded connections a'-n’.
As required, detailed embodiments of the present invention are disclosed herein; however, it is to be understood that the disclosed embodiments are merely exemplary of the invention, which can be embodied in various forms. Therefore, specific structural and functional details disclosed herein are not to be interpreted as limiting, but merely as a basis for the claims and as a representative basis for teaching one skilled in the art to variously employ the present invention in virtually any appropriately detailed structure. Further, the terms and phrases used herein are not intended to be limiting, but rather, to provide an understandable description of the invention.
The terms "a" or "an", as used herein, are defined as one or more than one. The term plurality, as used herein, is defined as two or more than two. The term another, as used herein, is defined as at least a second or more. The terms including and/or having, as used herein, are defined as comprising (i.e., open language, not excluding other elements or steps). Any reference signs in the claims should not be construed as limiting the scope of the claims or the invention.
It will be apparent to those skilled in the art that various modifications can be made to the threaded connection without departing from the scope as defined by the claims.

Claims (27)

-18- CONCLUSIES-18- CONCLUSIONS 1. Schroefdraadverbinding voor exploratie en productie van een koolwaterstofbron en die omvat: - een koppelorgaan dat een buitengelegen koppelingsdiameter COD heeft en dat omvat een eerste box-deel dat eerste binnengelegen schroefdraden omvat, een tweede box-deel dat tweede binnengelegen schroefdraden omvat, en een randdeel dat een zich radiaal uitstrekkende binnenrand omvat, waarbij het randdeel is opgesteld tussen het eerste box-deel en het tweede box-deel en een radiale randdeeldikte B heeft en een axiale randdeellengte C, en het eerste box-deel en het tweede box-deel een radiale box-deeldikte A hebben tussen respectievelijk de binnenrand en de eerste binnengelegen schroefdraden en de tweede binnengelegen schroefdraden, - een eerste buisvormig orgaan dat een eerste schroefdraadvrij buisdeel omvat en een eerste pin-deel dat eerste buitengelegen schroefdraden omvat, en - een tweede buisvormig orgaan dat een tweede schroefdraadvrij buisdeel omvat en een tweede pin-deel omvat dat tweede buitengelegen schroefdraden omvat, waarbij -- het eerste schroefdraadvrije buisdeel en het tweede schroefdraadvrije buisdeel een buitengelegen buisdiameter TOD en een radiale buiswanddikte W hebben, -- het eerste buisvormige deel en het tweede buisvormige deel een binnengelegen buisdiameter TID hebben, - de eerste binnengelegen schroefdraden, de tweede binnengelegen schroefdraden, de eerste buitengelegen schroefdraden en de tweede buitengelegen schroefdraden zwaluwstaartvormige schroefdraden hebben, - de eerste binnengelegen schroefdraden en de eerste buitengelegen schroefdraden zijn ingericht om een eerste binnengelegen primaire afdichting te vormen in finale opmaak, - de tweede binnengelegen schroefdraden en de tweede buitengelegen schroefdraden zijn ingericht om een tweede binnengelegen primaire afdichting te vormen in finale opmaak, en - de schroefdraadverbinding voldoet aan; COD > TOD B = ongeveer ((COD — TID) / 2)A threaded connection for exploration and production of a hydrocarbon well comprising: a coupling member having an outer coupling diameter COD and comprising a first box portion comprising first inner threads, a second box portion comprising second inner threads, and a edge portion comprising a radially extending inner edge, the edge portion being disposed between the first box portion and the second box portion and having a radial edge portion thickness B and an axial edge portion length C, and the first box portion and the second box portion have a radial box portion thickness A between the inner rim and the first inner threads and the second inner threads, respectively, - a first tubular member comprising a first thread-free tubular portion and a first pin portion comprising first outer threads, and - a second tubular member comprising a second threadless tube portion and a second pin portion comprising second outer threads, wherein -- the first threadless pipe portion and the second threadless pipe portion have an outer pipe diameter TOD and a radial pipe wall thickness W, -- the first tubular portion and the second tubular portion have an inner pipe diameter TID, the first inner threads, the second inner threads, the first outer threads and the second outer threads have dovetail threads, - the first inner threads and the first outer threads are arranged to form a first inner primary seal in final arrangement, - the second inner threads and the second outer threads are arranged to form a second inner primary seal in final configuration, and - the threaded connection conforms to; COD > TOD B = approximately ((COD — TID) / 2) -19- C>0,en A<W.-19- C>0, and A<W. 2. Schroefdraadverbinding volgens conclusie 1, waarbij de schroefdraadverbinding voldoet aan; C =£31,75 mm (1.25 inch), bij voorkeur C < 27,94 mm (1.1 inch).The threaded connection of claim 1, wherein the threaded connection satisfies; C = 31.75 mm (1.25 inch), preferably C < 27.94 mm (1.1 inch). 3. Schroefdraadverbinding volgens conclusie 1 of 2, waarbij de schroefdraadverbinding voldoet aan; C 26,35 mm (0.25 inch), bij voorkeur C = 10,16 mm (0.4 inch).The threaded connection of claim 1 or 2, wherein the threaded connection satisfies; C 26.35 mm (0.25 inch), preferably C = 10.16 mm (0.4 inch). 4. Schroefdraadverbinding volgens conclusie 1, waarbij de schroefdraadverbinding voldoet aan; 20,32 mm (0.8 inch) = C = 27,94 mm (1.1 inch), bij voorkeur C = 25,4 mm (10 inch).The threaded connection of claim 1, wherein the threaded connection satisfies; 20.32 mm (0.8 inch) = C = 27.94 mm (1.1 inch), preferably C = 25.4 mm (10 inch). 5. Schroefdraadverbinding volgens een van de voorgaande conclusies, waarbij de schroefdraadverbinding voldoet aan; A = 0,9W, bij voorkeur A < 0,8W.A threaded connection according to any one of the preceding claims, wherein the threaded connection satisfies; = = 0.9W, preferably A < 0.8W. 6. Schroefdraadverbinding volgens een van de voorgaande conclusies, waarbij de schroefdraadverbinding voldoet aan; A= 0,7W.A threaded connection according to any one of the preceding claims, wherein the threaded connection satisfies; A= 0.7W. 7. Schroefdraadverbinding volgens een van de voorgaande conclusies, waarbij de radiale box-deeldikte A is opgesteld bij de kritieke doorsnede van het eerste box- deel en het tweede box-deel.A threaded connection according to any one of the preceding claims, wherein the radial box part thickness A is arranged at the critical cross section of the first box part and the second box part. 8. Schroefdraadverbinding volgens een van de voorgaande conclusies, waarbij de schroefdraadverbinding voldoet aan; 114,3 mm (4.5 inch) < TOD = 244,48 mm (2 5/8 inch), bij voorkeur 114,3 mm (4,5 inch) < TOD s 193,68 mm (7.625 inch), meer bij voorkeur 114,3 mm (4.5 inch) < TOD s 139,7 mm (5.5 inch).A threaded connection according to any one of the preceding claims, wherein the threaded connection satisfies; 114.3 mm (4.5 inches) < TOD = 244.48 mm (2 5/8 inches), preferably 114.3 mm (4.5 inches) < TOD s 193.68 mm (7.625 inches), more preferably 114.3mm (4.5in) < TODs 139.7mm (5.5in). 9. Schroefdraadverbinding volgens een van de voorgaande conclusies, waarbij de schroefdraadverbinding voldoet aan: 6,3 mm (0.250 inch) = Ws 12,7 mm (0.500 inch), bij voorkeur 7,3 mm (0.290 inch) s W = 11,1 mm {0.437 inch).Threaded connection according to any one of the preceding claims, wherein the threaded connection satisfies: 6.3 mm (0.250 inch) = Ws 12.7 mm (0.500 inch), preferably 7.3 mm (0.290 inch) s W = 11, 1mm {0.437 inches). -20--20- 10. Schroefdraadverbinding volgens een van de voorgaande conclusies, waarbij; - in een eerste richting van de binnenrand en naar de eerste binnengelegen primaire afdichting beginnen de eerste binnengelegen schroefdraden en de eerste buitengelegen schroefdraden volledig contact te hebben bij een eerste afdichtingsstartpositie, - in een tegengestelde tweede richting van de binnenrand en naar de tweede binnengelegen primaire afdichting beginnen de tweede binnengelegen schroefdraden en de tweede buitengelegen schroefdraden volledig contact hebben bij een tweede afdichtingsstartpositie, - de eerste afdichtingsstartpositie is opgesteld bij een axiale afdichtingsafstand D van de tweede afdichtingsstartpositie, en - de schroefdraadverbinding voldoet aan; D>C.A threaded connection according to any one of the preceding claims, wherein; - in a first direction from the inner rim and towards the first inner primary seal, the first inner threads and the first outer threads begin to have full contact at a first seal start position, - in an opposite second direction from the inner rim and towards the second inner primary seal the second inner threads and the second outer threads begin to make full contact at a second seal start position, the first seal start position is arranged at an axial seal distance D from the second seal start position, and the threaded connection satisfies; D>C. 11. Schroefdraadverbinding volgens conclusie 10, waarbij de schroefdraadverbinding voldoet aan; 3,6 mm (0.142 inch) = (D -C)/2 £ 9,9 mm (0.392 inch), bij voorkeur 5 mm (0.2 inch) < (D —C)/2 57,7 mm (0.3 inch), meer bij voorkeur (D—C)/2 =6,1 mm (0.242 inch).The threaded connection of claim 10, wherein the threaded connection satisfies; 3.6 mm (0.142 inch) = (D -C)/2 £ 9.9 mm (0.392 inch), preferably 5 mm (0.2 inch) < (D -C)/2 57.7 mm (0.3 inch) , more preferably (D-C)/2 = 6.1 mm (0.242 inch). 12. Schroefdraadverbinding volgens een van de voorgaande conclusies, waarbij de zich radiaal uitstrekkende binnenrand is opgesteld tussen het eerste pin-deel en het tweede pin-deel.A threaded connection according to any one of the preceding claims, wherein the radially extending inner edge is disposed between the first pin portion and the second pin portion. 13. Schroefdraadverbinding volgens een van de voorgaande conclusies, waarbij het eerste buisvormige deel een eerste pin-neus omvat, waarbij het tweede buisvormige deel een tweede pin-neus omvat en waarbij in finale opmaak de eerste pin-neus en de tweede pin-neus zijn opgesteld op een afstand van de binnengelegen rand.A threaded connection according to any one of the preceding claims, wherein the first tubular portion comprises a first pin nose, the second tubular portion comprises a second pin nose and wherein in final arrangement the first pin nose and the second pin nose are arranged at a distance from the inner edge. 14. Schroefdraadverbinding volgens conclusie 13, waarbij de zich radiaal uitstrekkende binnenrand is opgesteld tussen de eerste pin-neus en de tweede pin-neus.The threaded connection of claim 13, wherein the radially extending inner rim is disposed between the first pin nose and the second pin nose. 15. Schroefdraadverbinding volgens een van de voorgaande conclusies, waarbij de schroefdraadverbinding in finale opmaak vrij is van enige verdere binnengelegen afdichting.A threaded connection according to any one of the preceding claims, wherein the threaded connection in final configuration is free of any further inner seal. -21--21- 16. Schroefdraadverbinding volgens een van de voorgaande conclusies, waarbij; - de eerste binnengelegen schroefdraden en de eerste buitengelegen schroefdraden samen een eerste schroefdraadstap vormen, en - de tweede binnengelegen schroefdraden en de tweede buitengelegen schroefdraden samen een tweede schroefdraadstap vormen.A threaded connection according to any one of the preceding claims, wherein; - the first inner screw threads and the first outer screw threads together form a first screw thread step, and - the second inner screw threads and the second outer screw threads together form a second screw thread step. 17. Schroefdraadverbinding volgens conclusie 18, waarbij de schroefdraadverbinding vrij is van enige verdere schroefdraadstap.The threaded connection of claim 18, wherein the threaded connection is free of any further threading step. 18. Schroefdraadverbinding volgens conclusie 18 of 17, waarbij de eerste schroefdraadstap en de tweede schroefdraadstappen taps toelopende schroefdraadstappen zijn.The threaded connection of claim 18 or 17, wherein the first thread step and the second thread steps are tapered thread steps. 19. Schroefdraadverbinding volgens een van de voorgaande conclusies, waarbij het koppelorgaan een eerste ontlastingsgroef omvat die is opgesteld tussen de eerste binnengelegen schroefdraden en de binnenrand en een tweede ontlastingsgroef omvat die is opgesteld tussen de tweede binnengelegen schroefdraden en de binnenrand.The threaded connection of any preceding claim, wherein the coupling member comprises a first relief groove disposed between the first inner threads and the inner rim and includes a second relief groove disposed between the second inner threads and the inner rim. 20. Schroefdraadverbinding volgens een van de voorgaande conclusies, waarbij de buitengelegen koppelingsdiameter COD de grootste diametrische afmeting van de schroefdraadverbinding is.A threaded connection according to any one of the preceding claims, wherein the coupling outer diameter COD is the largest diametrical dimension of the threaded connection. 21. Schroefdraadverbinding volgens een van de voorgaande conclusies, waarbij het randdeel een randbinnendiameter RID heeft en de schroefdraadverbinding voldoet aan: RID = TID + 0,127 mm (0.050 inch), bij voorkeur RID = TID.A threaded connection according to any one of the preceding claims, wherein the rim portion has a rim inner diameter RID and the threaded connection satisfies: RID = TID + 0.127 mm (0.050 inch), preferably RID = TID. 22. Schroefdraadverbinding volgens een van de voorgaande conclusies, waarbij het randdeel een randbuitendiameter ROD heeft en de schroefdraadverbinding voldoet aan; B = (ROD —RID)}/2.A threaded connection according to any one of the preceding claims, wherein the rim portion has a rim outer diameter ROD and the threaded connection conforms to; B = (ROD —RID)}/2. 23. Schroefdraadverbinding volgens een van de voorgaande conclusies, waarbij de schroefdraadverbinding voldoet aan; COD = ROD.A threaded connection according to any one of the preceding claims, wherein the threaded connection satisfies; COD = ROD. -22--22- 24. Schroefdraadverbinding volgens een van de voorgaande conclusies, waarbij het eerste box-deel een eerste buitengelegen box-diameter FBOD heeft, waarbij het tweede box-deel een tweede buitengelegen box-diameter SBOD heeft en waarbij de schroefdraadverbinding voldoet aan; COD = FBOD = SBOD.The threaded connection of any preceding claim, wherein the first box portion has a first outer box diameter FBOD, the second box portion has a second outer box diameter SBOD and wherein the threaded connection conforms to; COD = FBOD = SBOD. 25. Schroefdraadverbinding volgens een van de voorgaande conclusies, waarbij de schroefdraadverbinding een longitudinale as definieert.A threaded connection according to any one of the preceding claims, wherein the threaded connection defines a longitudinal axis. 28. Schroefdraadverbinding volgens conclusie 25, waarbij het randdeel en de binnenrand de longitudinale as volledig omgeven.The threaded connection of claim 25, wherein the rim portion and the inner rim completely surround the longitudinal axis. 27. Schroefdraadverbinding volgens een van de voorgaande conclusies, waarbij het randdeel een binnengelegen randoppervlak omvat dat bijna vlak, bij voorkeur vlak, is met een eerste binnengelegen buisoppervlak van het eerste buisvormige orgaan en een tweede binnengelegen buisoppervlak van het tweede buisvormige orgaan.A threaded connection according to any one of the preceding claims, wherein the rim portion comprises an inner rim surface which is nearly planar, preferably planar, with a first inner tube surface of the first tubular member and a second inner tube surface of the second tubular member.
NL2023800A 2019-07-12 2019-09-10 Threaded connection for exploration and production of a hydrocarbon well NL2023800B1 (en)

Priority Applications (9)

Application Number Priority Date Filing Date Title
NL2023800A NL2023800B1 (en) 2019-09-10 2019-09-10 Threaded connection for exploration and production of a hydrocarbon well
CN202080050120.6A CN114080486A (en) 2019-07-12 2020-07-13 Threaded connection for exploration and production of hydrocarbon wells
EP20746524.6A EP3997300A1 (en) 2019-07-12 2020-07-13 Threaded connection for exploration and production of a hydrocarbon well
MX2022000513A MX2022000513A (en) 2019-07-12 2020-07-13 Threaded connection for exploration and production of a hydrocarbon well.
PCT/US2020/041757 WO2021011443A1 (en) 2019-07-12 2020-07-13 Threaded connection for exploration and production of a hydrocarbon well
BR112022000485A BR112022000485A2 (en) 2019-07-12 2020-07-13 threaded connection
US17/626,396 US20220290784A1 (en) 2019-07-12 2020-07-13 Threaded connection for exploration and production of a hydrocarbon well
CA3144973A CA3144973A1 (en) 2019-07-12 2020-07-13 Threaded connection for exploration and production of a hydrocarbon well
CONC2022/0000056A CO2022000056A2 (en) 2019-07-12 2022-01-06 Threaded connection for the exploration and production of a hydrocarbon well

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Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0151574B1 (en) * 1983-04-29 1988-09-28 Hydril Company Improved tubular connection
US4917409A (en) * 1983-04-29 1990-04-17 Hydril Company Tubular connection

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0151574B1 (en) * 1983-04-29 1988-09-28 Hydril Company Improved tubular connection
US4917409A (en) * 1983-04-29 1990-04-17 Hydril Company Tubular connection

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