• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    THREADED TUBULAR CONNECTION. The present invention relates to a threaded tubular connection including a first tube and a second tube. The first tube includes a pin-shaped element that extends from an end of a main body of the first tube to an end end of the first tube. The second tube includes a box-like element that extends from an end of a main body of the second tube to an end end of the second tube. A cross-sectional area of a critical pin cross-section is within the limited range of approximately 5% of the cross-sectional area of a cross-section of each of the critical pin-and-box cross-sections is within the limited range of approximately 5% of the sum of the cross-sectional areas of an intermediate critical cross-section of the box-shaped element and an intermediate critical cross-section of the pin-shaped element.
    公开号:BR112013004282B1
    申请号:R112013004282-6
    申请日:2011-08-19
    公开日:2021-03-09
    发明作者:Russell ELDER；Bertrand Maillon
    申请人:Vallourec Oil And Gas France；Nippon Steel Corporation；
    IPC主号:
    专利说明:

    [0001] A threaded tubular connection is provided. More particularly, a threaded tubular connection with high tensile strength efficiency is provided.
    [0002] The present description refers to joints or sets of tubes to be joined by threads. The tubes described in this document are used in industry and, in particular, assemblies or threaded connections used in column-lines for tubing or for tubular production accessory lines or for a coating column or a subsurface coating [liner] or a ascending column for the operation or prospecting or exploration of oil or gas wells. The assemblies or screw connections described in this document can also be used for any purpose in which it is desirable to assemble pipelines or tubular accessories, such as, for example, in geothermal or thermoelectric installations. The threaded assembly described in this document is particularly useful in the assembly of metal tubes used as oil or gas well casing columns, or for so-called subsurface coatings in addition to the bottom of the casing column, as explained below.
    [0003] Various types of oil or gas transport tube assemblies are known to produce satisfactory results from the point of view of mechanical characteristics and impermeability, even under harsh conditions of use. Some of these sets imply the use of tubes equipped with male tapered conical threads at both ends, which are assembled by couplings having two corresponding female tapered conical threads. This form of assembly has the advantage of making the two components of the assembly rigid, due to the existence of positive interference that can be created between the male threads and the female threads.
    [0004] However, the outer diameter of these couplings is greater than that of the corresponding tubes and, when these sets are used with casing column tubes, the couplings require the drilling of holes with a larger diameter to accommodate the outer diameter of the couplings. In the case of very deep wells, with a depth greater than 4000 meters, the initial diameter of the first well lining columns and, consequently, the diameter of the well in the vicinity of the surface, can be twice as large using these couplings than what it would be necessary using thin couplings having an external diameter only slightly larger than the corresponding tubes of the coating columns.
    [0005] To avoid this difficulty, you can use sets without a coupling or sleeve. In this case, each of the tubular elements has an end with a male thread and an end with a female thread, constituting a fine set. These assemblies or unions are generally referred to as integral assemblies or unions, as opposed to assemblies or unions that employ a coupling or sleeve. The same need for integral joints is also met in the case of subsurface coatings that are suspended in the coating column at the bottom of it, are not cemented to the borehole and often extend horizontally to achieve the formation of oil or gas production. In particular, the exploitation of unconventional gas reservoirs, such as so-called shale gas reservoirs, requires a small diameter and subsurface coatings with integral joints.
    [0006] Integral assemblies are generally made up of tubes that include an expanded diameter at the end corresponding to the female threads and a reduced diameter at the end corresponding to the male threads. This is done in order to have sufficient material in the thickness of the tubes to ensure the geometric and mechanical resistance of the assembly that joins the tubes.
    [0007] It is also possible to reinforce the resistance of the male-female assembly using threads in two successive sections, or steps, instead of just a single one. Each threaded step has different thread diameters and is separated by a central ring-shaped zone. This contact area makes it possible to obtain a sufficient tightening of the threads, while at the same time, it prevents excessive screwing. In the case of threads with negative load flanks, the stop zone allows these threads to be tightened to their negative flanks and this reduces the risk of unscrewing due to the action of tensile stresses that may or may not be combined with strong pressures.
    [0008] An area of contact between threaded steps preferably has a high resistance in order to prevent the advance of the male element into the female element at a certain point, in order to avoid excessive screwing. In this case, the stop area acts as a central stop shoulder. This result can be achieved when the central stop zone is located in an area where the two components of the set have a large cross section and are configured so that they are firmly connected with each other.
    [0009] More complex central boss structures can be used between the threaded steps, in order to allow the central boss to also function as a seal. However, in order to obtain a good seal, it is necessary to have an elastic tightening of the surfaces in contact, because otherwise there is a risk that the tightening is due only to a plastic deformation. In this case, the joint quickly loses its watertight qualities during successive load variations (for example, internal pressure-external pressure cycles) or due to unscrewing operations. This loss of watertight capacity is essentially due to the fact that the surfaces are damaged by plastic deformation and even by seizing. SUMMARY OF EXAMPLIFICATIVE ASPECTS OF ADVANCES
    [00010] In one example, a threaded tubular connection is provided including a first tube (also called a first tubular element) and a second tube (also called a second tubular element). The connection can be, for example, a semi-embedded threaded connection. The first tube includes a pin-shaped element (also called a male tubular end) that extends from an end of a main body of the first tube to an end end of the first tube. The main body of the first tube can have a substantially constant inner diameter and outer diameter along an axial direction of the first tube. The pin-shaped element comprises two radially displaced sections (steps) of external threads. The two radially displaced sections of the external threads include a first thread section and a second thread section. The first thread section is separated from the second thread section by a first abutment surface, also called a central boss. The first thread section is located between the end end of the first tube and the first abutment surface, and the second thread section is located between the first abutment surface and the end of the main body of the first tube.
    [00011] The second tube includes a box-shaped element (also called a female tubular end), which extends from an end of a main body of the second tube to an end end of the second tube. The main body of the second tube can have a substantially constant inner diameter and outer diameter along an axial direction of the second tube. The box-like element includes two radially displaced sections (steps) of internal threads. The two radially displaced sections of internal threads include a third thread section and a fourth thread section. The third thread section is separated from the fourth thread section by a second abutment surface, also called the central boss. The third thread section is located between the end end of the second pipe and the second stop surface, and the fourth thread section is located between the second stop surface and the end of the main body of the second pipe.
    [00012] Each of the two tapered threaded steps includes a run-in entry part on one side of a respective end between the first tubular element and the second tubular element and a run-out exit part ] on the opposite side. Each inlet part in the first tubular element engages an outlet part of the second tubular element and each inlet part in the second tubular element engages in an outlet part of the first tubular element. An outer diameter of the box is not more than 10% (preferably not more than 6%) of a nominal outer diameter of the first and second tubular elements.
    [00013] The pin-shaped element has a critical pin cross section (PCCS) located on a threaded bottom of the second threaded section that is closest to the end of the main body of the first tube. The PCCS is subjected to a total stress transferred through all threads of the pin. The box-like element has a critical box cross-section (BCCS) located on a threaded bottom of the fourth threaded section that is closest to the end of the main body of the second tube. The BCCS is subjected to a total stress transferred through all threads in the housing. The box-like element has a critical intermediate box cross-section (BICCS) located on a threaded bottom of the third threaded section that is closest to the second stop zone of the second tube. The BICCS is subjected to a voltage transferred through the third thread section of the housing. The pin-shaped element has a critical intermediate pin cross section (PICCS) located on a threaded bottom of the first thread section that is closest to the first stop zone of the first tube. The PICCS is subjected to a voltage transferred through the first thread section of the pin.
    [00014] The first and second tubes satisfy the following ratios: The value of the PCCS is in the limited range of approximately ± 5% of BCCS and each of the values of PCCS and BCCS is in the limited range approximately ± 5% (BICCS + PICCS). BRIEF DESCRIPTION OF THE VARIOUS VIEWS OF THE DRAWINGS
    [00015] A more complete appreciation of the invention and many of its inherent advantages will be easily captured as it is better understood when using the detailed description that follows when considered in association with the accompanying drawings, in which: Figure 1 is a sectional view of a union with the tubular elements, male and female, mounted on each other; Figure 2 is a detailed cross-sectional view of the stop shoulder and the separate sealing part of the joint shown in Figure 1; Figure 3 is a detailed cross-sectional view of one of the thread inlet parts of the coupling shown in Figure 1; Figure 4 is a cross-sectional view of a joint that includes a central shoulder and end seals close to the terminal ends of the pin and the box; and, Figure 5 is a partial cross-sectional view along the X1-X1 axis of a male stem-conical threaded section profile. DETAILED DESCRIPTION
    [00016] Certain terminology used in the description that follows is for practical reasons only and is not limiting. The terms "joint" or "union" or "junction" are intended to have the same meaning in the description that follows, except for the situation in which each of these terms is used in a particular context that gives a particular meaning to the term. The term "tubes" is intended to encompass any type of tubes or tubular components or tubular accessories that currently exist or may be used in industry. The terms "back area" or "back surface" or "shoulder" are intended to have the same meaning in the description that follows, except where each of these terms is used in a particular context that gives a particular meaning to term.
    [00017] One solution, described in U.S. Patent No. 5,687,999, includes the positioning of two fluid-impermeable metal-to-metal sealing surfaces at the inner and outer ends of the joint, in addition to the ends of the threaded parts. The entire contents of U.S. Patent No. 5687999 are hereby incorporated by reference and Figures 2 and 3 of U.S. Patent No. 5687999 are reproduced as Figures 4 and 5 of the present disclosure.
    [00018] As shown in Figure 4, in this example, each male and female element has a region with two threaded sections, respectively, 4, 5 screw sections, for the male element 1 and 6, 7 screw sections for the element 2 female, between which there is an abutment surface with an annular or protruding shape 24. The central parts of these screw sections 4, 5 and 6, 7 are trunk-conical.
    [00019] The four sections 4, 5 of trunk-conical screwing of the male element and 6, 7 of the female element, have, in each of their ends, an area of escape threads (height decrease) in which the heights of the threads decrease to a value of zero. The decrease in the height of the threads can be achieved by machining the tops of the threads to a constant diameter in relation to the axis of the male or female element to generate a so-called exit thread part or by machining of screw bottoms with a constant diameter in relation to to the shaft to generate a so-called inlet thread part. When joining the two elements, male and female, their threads completely engage in the corresponding housings, both in the central parts of the threads and in the end areas with the escape threads.
    [00020] As shown in Figure 4, in these end zones, the tops and bottoms of the escape threads are limited in the direction from the outside or from the inside by the convergence of a diameter 16, 17 greater tapered cone or a diameter 18, 19 smaller tapered trunk, each of which extends the surface of the central part of the screw, and a diameter 20, 21 smaller cylindrical or a diameter 22, 23 larger cylindrical. It can be seen that the difference between the diameters of these 21 and 22 cylindrical surfaces corresponds to the radial height "D" of the ring-shaped or shoulder-back zone 24, in the central area of the set 3. This ring-shaped or shoulder-back zone 24 consists of the backing of the two surfaces of the element 1 male and element 2 female to each other.
    [00021] In the union illustrated in Figure 4, the back zone 24 does not have any waterproofing or sealing function. In particular, the abutment zone 24 does not provide a seal under all normal operating conditions of the assembly. Instead, two fluid-tight metal-to-metal seal surfaces 27 are arranged at the ends, inner and outer, of the joint, in addition to the ends of the threaded parts.
    [00022] As shown in figure 5, the load flanks of the male threads, such as 30, have a generating line with a negative A slope of approximately -3 ° to -20 °, in relation to a line that extends perpendicular to the X1-X1 axis of the element. After screwing, the cooperation between these threads with a negative load flank and the stop area 24 allows to tighten a male element 1 against a female element 2. This virtually eliminates the risk of splitting or splitting the threads.
    [00023] In the connection illustrated in Figures 4 and 5, the surfaces of the shoulder (or abutment zone) in the male and female elements, perpendicular to the X1-X1 axis, increase, for a given difference D radial, the mechanical strength of the joint. Consequently, it is also possible to give as great a value as possible to the critical thicknesses, E2 in element 1 male and El in element 2 female. The absence of watertight metal / metal surfaces in the central zone - central surfaces whose effectiveness is, as already explained, not satisfactory according to US Patent No. 5687999, due to the rigidity of this zone - makes it possible to bring the two sections together of tapering each other's trunk and, thus, improving, according to the aforementioned patent, the joint action between the two male and female elements.
    [00024] However, due to the radial space occupied by the sealing surfaces 27 and 28 located in thick wall locations in the connection shown in Figure 4, the high sealing properties of this connection do not give rise to a high efficiency of tensile strength. In particular, applicants have determined that the tensile strength efficiency of the connection shown in Figure 4 only achieves a tensile strength efficiency of 70 to 80%. The tensile strength efficiency of a connection is the ratio of the smallest "critical section" of the threads to the pipe body cross section and limits the performance of the connection. On the other hand, increasing the thickness of the ends of the male and female parts decreases the size of the central boss area and, therefore, reduces the resistance of the connection to compression.
    [00025] Figures 1-3 illustrate an exemplary connection that has a tensile strength efficiency of 90%, or more. As explained in more detail below, the present example does not use the central boss as a seal. In another aspect, the present example maximizes the tightening torque of the connection and its resistance to compression by employing a large shoulder area. The present example also employs threads with negative loading flanks to avoid the risk of the threads being unscrewed under tension, for example, in an oil well.
    [00026] Figure 1 shows a connection that includes a first tubular element and a second tubular element. The first tubular member is provided with a male tubular end 101 and the second tubular member is provided with a female tubular end 102. The male tubular end 101 of the first tubular element is called "pin" and the female end 102 of the second tubular element is called "box". The example in Figure 1 is a semi-embedded threaded connection, that is, a connection in which the outer diameter of the box is only slightly larger than the outer diameter of the tube, in which the two elements, pin 101 and box 102, are formed as the end . Each between pin 101 and housing 102 includes two tapered threaded steps and a rectilinear central boss 124. The pin includes a small diameter thread section 104 and a large diameter thread section 105. The box includes a small diameter thread section 106 and a large diameter thread section 107. The connection has an internal thread part (104, 106) and an external thread part (105, 107). Between these two parts, there is a sealing part 125 and a separate shoulder part 124.
    [00027] The configuration of the connection threads shown in Figure 1 is similar to that described in the example of Figures 4 and 5. Thus, each thread step comprises an entrance part, on the side of the free end (terminal end) of the element and a exit part on the opposite side. Each input part on pin 101 engages an output part on box 102 and each input part on box 102 engages an output part on pin 101. The input and output sections can be input / output sections. complete outlets or incomplete inlet / outlet sections, that is, in the latter case, the height of the threads does not decrease to zero. The rate at which the height of the threads decreases can also change along the inlet / outlet section to avoid a long threaded part. In addition, as will be discussed in more detail with reference to Figure 3, the transition point between the inlet and outlet sections of the engaged threads may not be in the same location.
    [00028] In order to increase the tensile strength efficiency of the connection illustrated in Figure 1, in addition to a two-step connection with inlet and outlet parts at the ends of each thread, this example includes a particular balance between four sections criticism of the connection. These sections include a critical pin cross section (PCCS) 171, a critical intermediate box cross section (BICCS) 172, a critical intermediate pin cross section (PICCS) 173, and a critical box cross cross section (BCCS) 174. PCCS 171 is a cross-sectional area of pin 101 (also called a tubular male end), which is subjected to a total stress transferred through all threads and which is located at a male tubular end 101 opposite the free end (terminal end) of the male tubular end 101. BCCS 174 is a cross-sectional area of the box (also called female tubular end) 102, which is subjected to a total stress transferred through all threads and which is located at one end of the female tubular end 102 opposite the end end of the end 102 female tubular. BICCS 172 is a cross sectional area of the female tubular end 102, which is subjected to a stress transferred through the external thread part 107 of the female tubular end 102 and which is located at one end of the external thread part 107 opposite the free end (terminal end) of the female tubular end 102. The PICCS is a cross-sectional area of the male tubular end 101, which is subjected to a stress transferred through the internal thread part 104 of the male tubular end 101 and which is located at one end of the internal thread part 104 opposite the free end ( end) of the male tubular end 101.
    [00029] If a cross-sectional area of one of these four critical stressed sections of the connection is not high enough, a break in that location may result. The PCCS and BCCS represent a risk of rupture near the end of, respectively, pin 101 and box 102. The combined PICCS and BICCS represent the risk of rupture by tension near the central boss 124. Applicants in the present application have recognized that improved tensile strength efficiency can be achieved by satisfying the following particular relationship: PCCS ~ (BICCS + PICCS) ~ BCCS In the present example, the symbol "~" means equal with a tolerance of ± 5%.
    [00030] The applicants recognized that the balance of efficiency between the four critical sections mentioned above in the form set out above maximizes and maintains the efficiency of the connection (~ 90%), while maximizing the rebound area, in order to obtain a greater torque resistance and also guarantee the axial performance of the connection.
    [00031] In addition, the relationship between critical sections may involve minor differences of 2% or even 1%. Preferably, the sum of PICCS and BICCS is greater than the highest value of PCCS and BCCS to avoid rupture near the central boss.
    [00032] As will be discussed, with regard to the comparative examples described below, the connection illustrated in Figure 4 does not follow the previously mentioned relationship between critical sections. Instead, the connection in Figure 4 presents ratios of lower critical connection sections (in% in relation to the pipe cross section) and, therefore, a tensile strength efficiency of the connection (that is, the smallest of the reasons. connection) which is less than for the example shown in Figures 1-3.
    [00033] In the connection of Figure 4, the radial space occupied by the surfaces 27, 28 seals at the thick ends of the element 1 male and element 2 female reduces the PCCS and BCCS. On the other hand, the example in Figures 1-3 includes a central seal configuration that allows the thick ends of the large diameter thread 105 on the pin and the small diameter thread 106 on the housing to be thicker than for the connection of Figure 4, without major inconveniences, and thus ensure the new relationship between
    [00034] As shown in Figure 2, the seal 125 of the present example is located in a central location, on the side, separate from the shoulder 124. A sealing surface 152 on pin 101 provides a seal, in the radial direction, with a surface 162 seal in box 102. The central boss surfaces 154 and 164, respectively, in box 102 and pin 103, are located between the two tapered thread steps and form stop bosses. Thus, when the connection is made, the shoulder surfaces 154 and 164 of the pin and housing are engaged and the sealing surfaces 152 and 162 of the pin and housing contact in a watertight manner, due to the radial interference between them. However, the shoulder surfaces 154 and 164 on the pin and housing are not designed to form a seal, even though they may be in watertight contact when the connection is not live. In particular, when the pin and housing are under experienced tension, typically during normal operation, the shoulder surfaces 154 and 164 do not form a seal.
    [00035] The choice of a single central seal in Figure 1, instead of two seals 27, 28 terminals in Figure 4, allows to reduce the radial space occupied by the seals and, then, to increase the PCCS, BCCS and / or the area of the bounce. This choice also makes the connection less sensitive to the risk of the pin coming off the housing, due to a pressure of lubricant in case of excessive application, the lubricant not being confined between end seals.
    [00036] The sealing surfaces 152 and 162 of the seal 125 can be tapered surfaces with a substantially equal inclination or one of the surfaces 152 and 162 can be a convex shaped domed surface, for example, a toric surface defined by a torus radius between 10 and 100 mm, and the other surface can be tapered. The inclination of the conical surface can be chosen between two limits, on one side, to limit the radial space occupied by the seal 125 and, on the other side, to limit the risk of seizing the sealing surfaces. For example, a seal slope of 1/6 (16.7%) can be selected.
    [00037] As shown in Figure 2, the surfaces of the box and the pin are configured to provide a radial clearance 181 between a surface 153 on the pin and the corresponding surface 163 on the box. These surfaces do not and cannot constitute a seal. The clearance 181 limits the interaction between the seal 125 and the stop shoulder 124 during an external load application. Specifically, the seal part 125 is separated from the shoulder 124 in order to limit the influence of the shoulder deformation on the seal part 125 during tension and compression, and therefore in order to maximize the performance of the connection under load conditions. cyclical. The axial clearance of the clearance 181 can be, for example, between 3 mm and 15 mm, and the radial clearance (radial clearance is half of the diametrical clearance which is the difference in diameter) can be comprised, for example, between 0.125 mm and 0.4 mm.
    [00038] Between the shoulder 124 and the major thread step, there are also surfaces 155 and 165 cylindrical, respectively, on pin 101 and box 102. There is also always a radial clearance 182 between these surfaces 155, 165 cylindrical. Cylindrical surfaces 155, 165 do not and cannot constitute a seal. The clearance 182 is a radial clearance that has a clearance comprised, for example, between 0.1 mm and 2 mm, in the clamping.
    [00039] A third gap, gap 183, is located between seal 125 and the threads on the opposite side to seal 125, rigid element to gap 181. The gap 183 is a radial gap that is formed between the cylindrical surfaces 151 and 161, respectively, at pin 101 and box 102. The clearance 183 has a clearance between, for example, 0.1 mm and 2 mm in the clamping.
    [00040] Minimizing clearances 182, 183 can increase either (PICC + BICCS) or the boss area, but it can make connection difficult.
    [00041] As mentioned above, the inputs of the pin and housing threads are based on the cylindrical - conical connection illustrated in Figure 4. The existence of a cylindrical - conical pin inlet on the outer thread section and a cylindrical - conical inlet on the internal thread section maximizes the boss area as follows: (cylindrical entry length * thread pitch) / 2 = boss height increase due to a part of the entry thread. As there is an input thread portion on each side of the boss 124 (one on the pin, the other on the housing), the increase in the total height of the boss will be the sum of the increases due to each input thread portion. Figure 3 illustrates a detailed cross-sectional view of one of the thread inlet parts of the coupling shown in Figure 1. Specifically, Figure 3 illustrates a thread outlet part 107 of housing 102 and a thread inlet part 105 of the pin 101. Lines 193 and 194 represented are lines that follow a tapered path, while lines 191 and 192 represent a cylindrical diameter. Pin bottoms on the inlet thread are tapered, although they are on a cylindrical surface limited by line 192, due to the shape of the machining insert.
    [00042] The transition point between the inlet and outlet section of engaged threads is not necessarily in the same location. In the example in Figure 3, the transition point between the cylindrical top of the box and the tapered top of the box is identified by reference J and the point of transition between the cylindrical function of the pin and the tapered bottom of the pin is identified by reference K. The cylindrical thread length of the inlet parts can be, for example, between 3 to 4 threads. With the connection of Figure 3, an additional amount of material G can be dedicated to the boss height, when compared to a case in which a conventional inlet thread bottom followed line 195 followed.
    [00043] The thread pitch can be comprised between 1/18 (5.555%) and 1/8 (12.5%). Selecting the thread pitch for each connection size helps to: 1. ensure the efficiency of the PCCS ~ (BICCS + PICCS) ~ BCCS connection; 2. ensure a sufficient thread area developed to avoid loosening; and 3. maximize the rebound height, to maximize torque capacity and / or resistance to compression loads or bending loads. The thread pitch can be different between two threads 104 (106) and 105 (107) stepped.
    [00044] The length of two threads, internal and external, can be the same or different, in order to maximize the efficiency of the intermediate cross sections. The length of the internal thread part can be, for example, 100% to 50% of the external thread part.
    [00045] In addition, the total developed thread area can be greater than 130%, but not more than 250% of the smallest critical section between PCCS and BCCS.
    [00046] The following tables compare the dimensions of a connection made according to the connection illustrated in Figure 4 with a connection made according to the connection illustrated in Figures 1-3. Table 1 is an example of the dimensions of four different connections built using the connection illustrated in Figures 1-3. As noted above, this connection can achieve a tensile strength efficiency of 90% or more. As can be seen in Table 1, the critical sections could differ from 3% to as low as 1%. In the tables that follow, PBCS refers to the nominal cross-sectional area of the pipe body (= π * (OD - pipe wall thickness) * (pipe wall thickness)). It should also be noted that the bounce area is systematically greater than 25%. The increase in the outer diameter in the housing defines a connection category (recessed / semi-embedded / std) and favorably influences the overall tensile strength efficiency of the connection and the torque of the shoulder area. As can be seen in Table 1, the examples are on the upper side of the possible range of an increase in the outer diameter for a semi-embedded type connection.
    Table 1. Exemplary Dimensions for Display Connection in


    [00047] Table 2 is an example of the dimensions for four different connections built using the connection illustrated in Figure 4. As noted above, this connection can only achieve a tensile strength efficiency of 70-80% or more. As can be seen in Table 2, the critical sections can have differences that are as high as 9% and 10%. This connection also obtains a bounce area between 20 and 25%, less than for the connection of Figures 1-3. Table 2. Comparative Dimensions for the Connection Shown in Figure 4.
    [00048] Obviously, numerous modifications and variations of the present invention are possible in light of the previous teachings. It should therefore be understood that, within the scope of the appended claims, the invention can be implemented in a manner other than that specifically described in this document.
    [00049] In particular, other types of shoulders other than the rectilinear shoulder 124 of Figure 1 can be used, for example, an inverted shoulder can be used having a negative angle of 20 ° or less in relation to a perpendicular to the axis of connection.
    [00050] Hook threads in Figure 5 can also be replaced by other thread profiles.
    [00051] Dry lubrication can also be used in place of the conventional compound lubricant (RP API 5A3) to implement small clearances 182, 183 radial.
    权利要求:
    Claims (15)
    [0001]
    1. Threaded tubular connection, characterized by the fact that it comprises: a first tube, the first tube including a pin-shaped element (1, 101) extending from one end of a main body of the first tube to an end end of the first tube , including the pin-shaped element two radially displaced sections of external threads (4, 104, 5, 105), including the two radially displaced sections of external threads a first thread section (4, 104) and a second thread section (5, 105), the first thread section being separated from the second thread section by a first abutment surface (24, 124, 154), the first thread section being located between the end end of the first tube and the first surface stop and the second thread section being located between the first stop surface and the end of the main body of the first tube; and, a second tube, the second tube including a box-like element (2, 102) extending from one end of a main body of the second tube to an end end of the second tube, the box-like element including two displaced sections radially of internal threads (6, 106, 7, 107), including the two radially displaced sections of internal threads a third thread section (6, 106) and a fourth thread section (7, 107), the third section being thread separated from the fourth thread section by a second abutment surface (24, 124, 164), the third thread section being located between the end end of the second tube and the second abutment surface and the fourth thread section being located between the second abutment surface and the end of the main body of the second tube, wherein the pin-shaped element includes a critical pin cross section (PCCS) located on a threaded bottom of the second most threaded section near the end of the main body of the first tube, the box-like element includes a critical box cross section (BCCS) located on a threaded bottom of the fourth thread section that is closest to the end of the main body of the second tube, the box-like element includes an intermediate box cross-section (BICCS) located on a threaded bottom of the third thread section that is closest to the second stop zone of the second tube and the pin-like element includes a cross section intermediate pin criticism (PICCS) located on a threaded bottom of the first thread section that is closest to the first stop zone of the first tube, and where the first and second tubes satisfy the following relationships: the PCCS value lies it is in the limited range between + 5% and -5% of BCCS and, each of the values of PCCS and BCCS is in the limited range between + 5% and -5% (BICCS + PICCS), where the pin includes a first the central sealing surface (152) located between the first thread section and the first abutment surface and the housing includes a second central sealing surface (162) located between the fourth thread section and the second abutment surface, and, where , in a threaded state, the first central sealing surface engages with the second central sealing surface, in a radial direction, so as to form a fluid-tight seal (125) that extends in an axial direction of the threaded tubular connection and is separate and distinct of the first and second abutment surfaces.
    [0002]
    Threaded tubular connection according to claim 1, characterized in that, in the threaded state, the fluid-tight seal is separated from the first and second abutment surfaces in the axial direction of the threaded tubular connection by a first part of clearance (181), the pin and the box being spaced apart from each other, in the radial direction, in the first gap part so as to form a first gap between the pin and the box in the first gap part.
    [0003]
    Threaded tubular connection according to claim 2, characterized in that the first clearance includes an axial clearance between 3 mm and 15 mm, and a radial clearance between 0.125 mm and 0.4 mm.
    [0004]
    Threaded tubular connection according to claim 3, characterized in that, in the threaded state, the threaded tubular connection includes a second gap part (182), the second gap part being located between the second abutment surface and the third thread section on the box, and between the first abutment surface and the second thread section on the pin, the pin and the box being spaced apart from each other, in the radial direction, in the second clearance part so as to form a second gap between the pin and the housing in the second gap part, and where, in the threaded state, the threaded tubular connection includes a third gap part (183), the third gap part being located between the second central sealing surface and the fourth box thread section, and between the first central sealing surface and the first thread section on the pin, the pin and the box being spaced apart, in the radial direction, in the third clearance part so as to form a third gap between the pin and housing in the third clearance part.
    [0005]
    Threaded tubular connection according to claim 1, characterized in that the first, second, third and fourth thread sections each include threads having a negative slope loading flank.
    [0006]
    6. Threaded tubular connection according to claim 1, characterized by the fact that the first, second, third and fourth thread sections are each tapered-conical and each include an inlet thread portion in a first end, an outlet thread part at a second end and a full height thread part between the inlet thread part and the outlet thread part.
    [0007]
    Threaded tubular connection according to claim 6, characterized in that an inclination of each of the first, second, third and fourth thread sections is in the range between 1/18 and 1/8.
    [0008]
    Threaded tubular connection according to claim 6, characterized in that the outlet thread part of at least one of the first, second, third and fourth thread sections is a partial outlet thread.
    [0009]
    Threaded tubular connection according to claim 7, characterized in that a length of the first and fourth threads is equal to a length of the second and third threads.
    [0010]
    Threaded tubular connection according to claim 6, characterized in that a length of the first and fourth threads and fourth is in the range of 50% to 100% of a length of the second and third threads .
    [0011]
    11. Threaded tubular connection according to claim 1, characterized by the fact that each of the PCCS and BCCS is in the limited range between + 3% and -3% (BICCS + PICCS).
    [0012]
    12. Threaded tubular connection according to claim 11, characterized by the fact that each of the PCCS and BCCS is in the limited range between + 2% and -2% (BICCS + PICCS).
    [0013]
    13. Threaded tubular connection according to claim 1, characterized by the fact that (BICCS + PICCS) is greater than PCCS and BCCS.
    [0014]
    14. Threaded tubular connection according to claim 1, characterized in that the tensile strength efficiency of the threaded tubular connection is at least 90%.
    [0015]
    15. Threaded tubular connection according to claim 6, characterized in that an inclination of the first thread section is different from the inclination of the second thread section.
    类似技术:
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    同族专利:
    公开号 | 公开日
    PL2609279T3|2018-10-31|
    AU2011295130B2|2015-10-01|
    CN103140645B|2019-05-07|
    US10215314B2|2019-02-26|
    EP2609279A2|2013-07-03|
    JP5908905B2|2016-04-26|
    AU2011295130A1|2013-02-21|
    CA2807087C|2018-05-22|
    BR112013004282A2|2016-05-31|
    MX364135B|2019-04-12|
    EA025974B1|2017-02-28|
    JP2013536339A|2013-09-19|
    EA201370043A1|2013-07-30|
    EP2609279B1|2018-05-16|
    WO2012025461A3|2013-03-14|
    MX2013002180A|2013-05-06|
    CA2807087A1|2012-03-01|
    MY174579A|2020-04-28|
    CN103140645A|2013-06-05|
    US20130015657A1|2013-01-17|
    WO2012025461A2|2012-03-01|
    US10145495B2|2018-12-04|
    UA110034C2|2015-11-10|
    AR082715A1|2012-12-26|
    US20120043756A1|2012-02-23|
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    法律状态:
    2017-09-26| B25D| Requested change of name of applicant approved|Owner name: NIPPON STEEL AND SUMITOMO METAL CORPORATION (JP) , |
    2018-12-26| B06F| Objections, documents and/or translations needed after an examination request according [chapter 6.6 patent gazette]|
    2019-07-30| B06U| Preliminary requirement: requests with searches performed by other patent offices: procedure suspended [chapter 6.21 patent gazette]|
    2019-09-03| B25D| Requested change of name of applicant approved|Owner name: VALLOUREC OIL AND GAS FRANCE (FR) ; NIPPON STEEL C Owner name: VALLOUREC OIL AND GAS FRANCE (FR) ; NIPPON STEEL CORPORATION (JP) |
    2019-12-31| B06A| Patent application procedure suspended [chapter 6.1 patent gazette]|
    2020-04-22| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|
    2020-06-02| B09X| Republication of the decision to grant [chapter 9.1.3 patent gazette]|
    2020-11-24| B09W| Correction of the decision to grant [chapter 9.1.4 patent gazette]|Free format text: RETIFICACAO DO QUADRO 1 |
    2021-03-09| B16A| Patent or certificate of addition of invention granted [chapter 16.1 patent gazette]|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 19/08/2011, OBSERVADAS AS CONDICOES LEGAIS. |
    优先权:
    申请号 | 申请日 | 专利标题
    US12/861,497|US10215314B2|2010-08-23|2010-08-23|Tubular threaded connection|
    US12/861,497|2010-08-23|
    PCT/EP2011/064299|WO2012025461A2|2010-08-23|2011-08-19|Tubular threaded connection|
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