• 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 CONNECTION. The present invention relates to a threaded connection 1 comprising a first and a second tubular component, the first component comprising a male end comprising a distal surface and a threaded region 5 arranged on its outer peripheral surface, the second component comprising a female end comprising a distal surface and a threaded zone 4 arranged on its inner peripheral surface, the threaded zone 5 of the male end being threaded into the threaded zone 4 of the female end, the threaded zones 4 and 5 comprising the respective male and female threads 40 , 50 having a width that increases from the distal surface, the threads comprising load flanks having negative angles in at least part of their radial dimension, and penetration flanks, with a radial gap remaining in the bonded state between the ridges of the threads male and the roots of the female threads and / or between the crests of the female threads and the roots of the m threads I think, with a radial clearance remaining in the connected state between the penetration flanks of the male and female threads, and the distal surface of the male end and / or the female end being brought into contact with the axial slope against a corresponding abutment surface.
    公开号:BR112012012134B1
    申请号:R112012012134-0
    申请日:2010-11-09
    公开日:2020-12-29
    发明作者:Pierre Martin；Bertrand Maillon
    申请人:Vallourec Oil And Gas France；Nippon Steel Corporation；
    IPC主号:
    专利说明:

    The present invention relates to the field of watertight connections for tubular components, used in particular for drilling or operating hydrocarbon wells. During drilling or operation, the connections are subject to high compressive and tensile stresses and must not be separated.
    Such connections are subject to compression and axial tensile stresses, internal or external fluid pressure stresses, flexural or even torsional stresses, possibly combined and with an intensity that can vary. The watertightness must persist despite efforts and harsh conditions on the spot. Threaded connections must be capable of being made and broken several times without degradation of performance, in particular by localized mutual friction accompanied by particle removal. After opening, the tubular components can be reused under other service conditions.
    Under tension, a phenomenon called “jumping out” can occur and spread from one thread to another, at the risk of the connection breaking apart. This phenomenon is facilitated by a high internal pressure.
    The invention proposes an improved connection with regard to its tensile behavior.
    The threaded connection comprises a first and a second tubular component. The first component comprises a male end provided with an outer peripheral surface comprising a threaded area, a sealing surface and then an axial abutment surface. The second component comprises a female end provided with an inner peripheral surface comprising an axial shoulder, a sealing surface and a threaded area. The threaded area of the male end is threaded inside the threaded area of the female end so that the respective sealing surfaces are in contact with each other and so that the respective abutment surfaces are in contact. The threaded areas are provided with threads comprising a root, a crown, a penetration flank and a load flank, with an axial gap remaining between the threaded crowns and the roots in the connected state and with a radial gap subsisting between the penetration flanks in the on state. The axial dimension of the threads varies. The loading flank and the penetrating flank have negative angles over at least part of their radial dimension.
    The term ’’ threading ”represents the operation of rotation and relative translation of one component in relation to another with mutual engagement of the threaded zones. The term "connection" or "execution" means the operation that follows the threading, continuing the rotation and relative translation, resulting in an execution torque given between the two components. The angle of the flanks is measured in a clockwise direction in relation to a radial plane that passes through the base of the flanks at the level of the curvature that connects with the root.
    Other features and advantages of the invention will become apparent from the detailed description and drawings that follow, in which: Figure 1 shows a first longitudinally threaded connection diagrammatically; figure 2 shows diagrammatically a second threaded connection in longitudinal section; figure 3 shows diagrammatically a threaded area of the connection in longitudinal section in reduced view; figure 4 shows diagrammatically a detail of the threaded area of the connection; and figure 5 diagrammatically shows an end of the male part.
    The attached drawings are not only used to complete the invention but also, if necessary, to contribute to its definition.
    In order to improve connections, the applicant has developed better connections, called premium connections, which go beyond API standards. As an option, sealing surfaces adjacent to the threaded areas can be provided, said surfaces being brought into interference contact when they are threaded from the components.
    Threaded zones are provided at the end of each of the male and female tubular components. The female tubular component can be a long tube or, on the contrary, a short coupling type tube. The sealing against high pressure fluids (liquids or gases) thus results in bringing the sealing surfaces into a radially mutual interference contact. The intensity of the radial interference contact is a function of the relative radial positioning of the male and female threaded zones, said relative positioning being determined by the contact of the abutment surfaces provided respectively at the male and female ends.
    Relative positioning results from contact of the contact points. The abutment surfaces are provided on the internal surface of the connection. At its outer periphery, the male end comprises a threaded area that extends over a sealing surface which, in turn, extends over a terminal part that ends up at a stop surface that is oriented radially in relation to the axis of connection revolution. In its internal periphery, the female end comprises a threaded zone that extends over a sealing surface which itself extends through a terminal part that ends in a back surface that is oriented radially in relation to to the axis of revolution of the connection. The connection therefore has a double backrest. Other connections have a single backrest, radially external to the threaded zone or internally to the threaded zone.
    The applicant is particularly focused on large diameter threaded connections with a diameter greater than 300 mm, more particularly greater than 375 mm. These connections are occasionally subjected to intense tensile and compression loads. Thus, it is desirable that the connection performs well under tension and compression. When the tensile load is excessive, the threads can separate from each other by a disengagement phenomenon that forces the two components of the connection to separate. The consequences can be particularly uncomfortable from both a technical and cost perspective. This is particularly the case when the thread has a tapered generatrix; the phenomenon of “popping out” of a thread can cause the connection to separate completely.
    U.S. 4,822,081 describes a thread for male and female connections used in oil exploration tubes. The threads are of the self-locking type with contact between the flanks when the shoulders and the end surfaces are even in contact. The back surfaces are inclined at different angles. The threads are also self-tightening in the radial direction. This type of self-locking and self-tightening threaded connection requires a very high execution torque that is difficult to achieve for large diameter pipes. Since the free volume in the thread is too low, the thread can cause the grease to be under high pressure, which can cause leakage. Since the axial positions of the abutment surfaces in relation to the threads are uncertain due to industrial tolerances, they can result in poor positioning of the welding surfaces and consequently a leak. The end of the threading operation is only able to be detected by determining an upper torque limit, due to the absence of a positive stop during the threading operation. The backrests are hit during the final run. Excessive thread execution torque can result in plastic deformation of the sealing surfaces, which perniciously affects the sealing of the connection.
    US-5 462 315 describes a tubular connection with a central seal between two parts of the thread. The loading flanks of the threads are in mutual contact after the thread is made. The disadvantages are essentially the same as for the previous type.
    US-2002/27363, EP-1 046 179 and EP-1 302 623 provide for contact of the threaded flanks after the connection is made.
    JP 2002/081584 discloses a thread profile with hook co-operation. These hooks support all tensile loads and radial displacement loads, which can cause damage to the threads with cyclic, repetitive forces. Traction loads must remain low due to the small surface area through which they are transmitted. The penetration flanks are strongly inclined, which is harmful to the compression effort. High threading torque is required due to interference between crowns and thread valleys.
    The applicant has developed a connection that greatly reduces the risk of "popping out" regardless of the position of the thread, with a low thread execution torque, which allows the loading surfaces to be positioned properly and there is enough space for the grease. An axial clearance between the penetration flanks is present in the connected state, that is, after thread execution, and there is also an axial clearance present between the roots and crowns of the thread. The loading flanks of the threads are at a negative angle. thread penetration flanks are at a positive angle, a backrest allows the sealing surfaces to be properly positioned.
    As can be seen in figure 1, a threaded tubular connection 1 comprises a female end 2 and a male end 3. The female end 2 and / or the male end 3 can belong to a tube several meters long, for example from 10 to 15 meters long. One end, usually female, can constitute the end of a coupling, in other words, a short tube, allowing two tubes of great length to be connected together, each one equipped with two male ends (coupled and threaded connection). known as the T&C link). The coupling can be donated with two female ends. In a variation, a long pipe with a male end and a female end (integral threaded connection) can be supplied. Connection 1 is the type produced massively in the industry.
    Link 1 can be used to form casing chains or tubing chains for hydrocarbon wells, or chains for lifting excess tubes or drilling tubes for the same wells.
    The tubes can be produced in different types of non-alloy, low-alloy or high-alloy steel, or even in ferrous and non-ferrous alloys, which are heat treated or cold worked depending on their service conditions, such as , for example: the level of mechanical stress, the corrosive nature of the fluid inside or outside the tubes, etc. It is also possible to use steel tubes of low corrosion resistance coated with a protective layer, for example an alloy that is resistant to corrosion or a synthetic material.
    The female threaded end 2 comprises a female threaded zone 4. The female threaded zone 4 is conical, for example with a half-angle in the range 0.5 ° to 3rd, preferably in the range 1st to 2nd. The female threaded zone 4 is arranged inside the female element 2. The male end 3 comprises a male threaded zone 5 arranged on an external surface of said male end 3. The male threaded zone 5 is coupled with the female threaded 4. The male threaded zone 5 has a taper that is essentially the same as that of the female threaded zone 4. On the opposite side of the abutment surfaces 7 and 8 in relation to the threaded zones 4 and 5, the female end 2 comprises a distal surface 6 which is essentially perpendicular to axis 20 of the connection. The term "distal surface" means a surface located between a threaded area, continuous or non-continuous, and the free end of the element, male or female. The distal surface can be located at said free end. In this case, the distal surface 6 is terminal.
    The female threaded zone 4 extends until it is adjacent to the end surface 6. In the connected state, the end surface 6 is separated from any essentially optional radial surface of the male end 3, in particular a shoulder, by at least 0.1 mm, for example.
    The distal surface of the male end 3 is in the form of an annular surface, in this case tapered. The distal surface forms an axial abutment surface 7 which limits the relative axial movement between the female end 2 and the male end 3. The abutment surface 7 is in contact against the shoulder of the female end 2 which also forms a surface backrest 8, in this case conical. The abutment surface 7 can be radial or inclined at an angle up to 45 ° to a radial plane. In the example shown in figure 1, the angle is in the range of 15 ° to 25 °.
    Between the threaded area 4 and the contact surface 8, the female end comprises an essentially tapered surface 12 and optionally a recess 10, see figure 5. The recess 10 can have an essentially cylindrical surface 14 and a revolution surface 18 disposed between the threaded area 4 and the essentially tapered surface 12. The essentially tapered surface 12 is adjacent to the abutment surface 8. The recess 10 can act as a reservoir for grease when the grease is expelled from between the zones threads 4 and 5, when threading. As can be seen in figure 1, at least a hollow part of the threaded area 4 adjacent to the essentially cylindrical surface 14 is free in the connected state and participates in the collection of excess grease. The revolution surface 18 connects the essentially cylindrical surface 14 to the abutment surface 8. The abutment surface 8 can have a conical shape as in EP-0 448 912, a toroidal shape as in US-3 870 351 or in WO-2007/017082, or multi-storey as in US-4 611 838, with a protuberance as in US-6 047 797, or a combination of these. The reader is invited to refer to these documents.
    The male end 3 comprises a lip 9 which extends axially beyond the male threaded area 5 to the abutment surface 7. The outer side of the lip 9 comprises an essentially conical surface 13 with an axial length slightly longer than the length - axial length of the revolution surface 12, which is essentially conical, of the female end 2. A part of the revolution surface 13 and a part of the revolution surface 12 are in contact with each other in radial interference at the connected position of the illustrated connection 1 in the figures. The revolution surfaces 12 and 13 that form the sealing surfaces prevent fluid movement between the inside and outside of the connection. The taper angle of the sealing surfaces can be in the range of 1 to 45 °, preferably in the range 3 to 20 °, for example 6 °. The taper angle of the sealing surfaces can be greater than the taper angle of the threaded areas. The connection comprises an axial stop that ensures the precise positioning of the sealing area formed by the revolution surfaces 12 and 13 in the connected state.
    The modality of figure 2 is similar to the previous modality, with the exception that the backing surfaces 7 and 8 of the female end 2 and male end 3 are arranged on the radially external side of the connection. The abutment surfaces 7 and 8 are arranged between the female 4 and male 5 threaded areas and the outer surface of the connection 1. The female end 2 comprises a sealing surface 12 adjacent to the abutment surface 8 and a sealing surface 14 distal to the abutment surface 8. The sealing surface 14 is arranged between the threaded area 4 and the cavity of the female end 2. The sealing surface 14 is essentially tapered, for example at an angle in the range of 1st to 45 ° . The sealing surface 12 is domed and annular, for example an arc of axial cross-section.
    The male end 3 comprises a sealing surface 13 adjacent to the abutment surface 7 and a sealing surface 15 distal from the abutment surface 7. The sealing surface 13 is in watertight contact with the sealing surface 12 in the connected state or adjusted. The sealing surface 15 is arranged between the male threaded zone 5 and the cavity of the male end 3. The sealing surface 15 is essentially tapered, for example, with an angle in the range of 1st to 45 °. The angle of the sealing surface 15 is less than the angle of the sealing surface 14. The sealing surface 15 is in watertight contact with the sealing surface 14 in the connected or adjusted state.
    The lip 9 of the male end 3 comprises an essentially radial end surface 17 which extends between the vane 15 and the cavity of the male end 3. The end surface 17 can have a radial dimension in the range of 0.5 mm to 16 mm depending on the diameter of the tube which can itself be up to 550 mm, although it is preferably more than 300 mm, more preferably 350 mm. In the connected state, the terminal surface 17 is at least 0.1 mm away from any essentially radial surface of the female end 2, for example. The connection comprises an axial stop that provides the precise positioning of the two sealing zones formed by the sealing surfaces 12 and 13 on the one hand and 14 and 15 on the other, in the connected state.
    As can be seen in figures 3 and 4 corresponding to the two previous embodiments, the female threaded area 4 comprises threads 40 with an axial length adjacent to the crown which is greater than the axial length adjacent to the base. The male threaded zone 5 comprises threads 50 with an axial length adjacent to the crown which is greater than the axial length adjacent to the base. The angle of inclination of a thread penetration flank is positive in a clockwise direction, the angle being measured in relation to a radial plane perpendicular to the connection axis. The angle of inclination of a loading flank of a thread is negative in a clockwise direction, the angle being taken in relation to a radial plane perpendicular to the connection axis. In a modality, the threads 40, 50 have a dovetail profile. Alternatively, the angle of inclination of a loading flank is different from the angle of inclination of a penetrating flank. The angle of inclination of a penetration edge of the female threaded zone 4 is essentially equal to the angle of inclination of a penetration edge of the male threaded zone 5. The angle of inclination of a load flank of the female threaded zone 4 is essentially the same as inclination angle of a load flank of the male threaded zone 5.
    A thread 40, 50 comprises a crown 41, 51, a root 42, 52, a loading flank 43, 53 and a penetration flank 44, 54. Connection bends are provided between the flanks and the crown and between the flanks and the root. The width of crowns 41, 51 and roots 42, 52 varies as a function of the position of the corresponding thread along the axis of the tube. Said width L can be expressed as follows: L = L0 + Ax in which Lo and A are constant and x is the position along the axis. The width is measured parallel to the connection axis 1. The diameter of the crowns 41, 51 and roots 42, 52 varies as a function of the corresponding thread position along the pipe axis due to the taper of the thread. Crowns 41, 51 and roots 42, 52 of threads 40, 50 are parallel to the axis of the threaded connection. This facilitates machining and engagement during the execution of the threaded connection.
    The male threaded zone 5 may have a first part in which the width of its teeth increases from a value corresponding to the width of the tooth closest to the terminal surface of the male end to a value corresponding to the width of the tooth furthest from said surface terminal, while the tooth width of the female threaded zone 4 decreases from a value corresponding to the width of the tooth furthest from the terminal surface of the female end to a value corresponding to the width of the tooth closest to said terminal surface, so that the threaded areas 4, 5 cooperate in the execution of the connection to leave an axial gap between the penetration flanks.
    The ratio between the width of the tooth closest to the end surface of the male end and the width of the tooth furthest from the end surface of the female end may be in the range 0.1 to 0.8.
    In the connected state (after adjustment), a radial clearance is present between the crowns 41 of the threads 40 of the female threaded zone 4 and the roots 52 of the threads 50 of the male threaded zone 5. The radial clearance is in the order of 0.05 mm at 0.5 mm. The choice of radial clearance in the connected state can be guided by the desired volume of grease and machining tolerances. A clearance of 0.15 mm or less is desirable when machining quality is high. In the connected state, a radial clearance, which is visible in figure 4, is present between the roots 42 of the threads 40 and the crowns 51 of the threads 50. The radial clearance is in the range of 0.05 mm to 0.5 mm.
    In the connected state (after adjustment), a radial clearance, which is visible in figure 4, is present between the penetration flanks 44 and 54 respectively of the threads 40 of the female threaded zone 4 and of the threads 50 of the male threaded zone 5. The axial clearance is in the range of 0.02 mm to 1 mm. Choosing the axial clearance in the connected state can be guided by the desired volume of grease, the angle of the flanks and the machining tolerances. A clearance of 0.05 mm or less is desirable when high-quality machining is carried out and the flank angle has an absolute value of 5 ° or less. The load flanks 43 and 53 support the interference loads after adjustment.
    The loading edge 43 of the threads 40 of the female threaded zone 4 is inclined with respect to a radial plane in order to interfere with the corresponding inclined loading edge 53 of the threads 50 of the male threaded zone 5 in the case of elastic deformation of the connection, in particular under traction, or without internal pressure. The interference is radial in order to preserve the connection between the threads. The threads mutually form radial retention hooks. The slope of the loading edge 43 is in the range of -1 ° to -15 °. Above -1o, the effect of radial retention becomes low. Below -15 °, the compression stress can be affected. A preferred range is -3o to -5o. The inclination of the loading edge 53 of the threads 50 of the male threaded zone 5 is located at the same preferred main intervals. The inclination of the loading edge 53 may be equal to or different from the inclination of the loading edge 43, for example, approximately 3 °.
    The penetration flank 44 of the threads 40 of the female threaded zone 4 is inclined with respect to a radial plane in order to interfere with the corresponding inclined penetration flank 54 of the threads 50 of the male threaded zone 5 in the case of elastic deformation of the connection, particularly under traction load, with or without internal pressure. The interference is radial in order to preserve the connection between the threads. The threads mutually form radial retention hooks. The slope of the infeed flank 44 is in the range of 1 to 15 °. Below 1st, the radial retention effect becomes low. Above 15 °, the compression effort can be affected. A preferred range is 3 ° to 5 °. The slope of the penetration flank 54 of the threads 50 of the male threaded zone 5 is located at the same preferred main intervals. The slope of the penetration flank 54 can be equal to or different from the slope of the penetration flank 44, for example, approximately 3 °.
    The slope of the infeed flank 44 can be the same or different from the slope of the loading flank 43, for example approximately 3 °. The inclination of the infeed edge 54 can be the same or different from the inclination of the loading edge 53, for example, approximately 3 °.
    The connection curvatures can be in the range of 0.005 mm to 3 mm. The connection curves reduce the stress concentration at the foot of the load flanks and thus improve the fatigue behavior of the connection.
    The female 4 and male 5 threaded areas can constitute multiple inlet threads, preferably a double inlet thread. This makes the thread run faster.
    The flanks may have a dovetail profile. The geometry of dovetail threads increases radial stiffness when they are attached, compared to threads with an axial width that reduces the stability of the base to the crown of the threads.
    The flanks can have a trapezoidal profile. The axial clearance between the penetration flanks can be in the range of 0.002 mm to 1 mm, preferably in the range of 0.05 mm to 0.5 mm.
    Radial clearance can be provided at the roots of the threads of a first component and / or at the crowns of the threads of a first component. The radial clearance can be in the range of 0.05 mm to 0.5 mm, preferably in the range of 0.05 mm to 0.15 mm.
    The load flanks can be at an angle in the range of -1 ° to -15 °, preferably in the range of -3 ° to -5 °. The penetration flanks can be at an angle in the range of 1 to 15 °, preferably in the range of 3 to 5 °. The loading flanks may be at a different angle than the infeed flanks.
    The abutment surfaces in mutual contact may be at an angle in the range 0 ° to 45 °, preferably in the range 5 ° to 20 °, with respect to a radial plane.
    Threaded zones can constitute multiple entry threads, such as double entries, for example.
    The male end may comprise between its distal surface and its threaded area (5), a metal / metal sealing surface cooperating with a corresponding sealing surface provided on the female end.
    The female end may comprise between its distal surface and its threaded area (6), a metal / metal sealing surface cooperating with a corresponding sealing surface provided on the male end.
    The threaded zones can have a conical generatrix with an inclination in the range 4% to 5%.
    The invention is not limited to the examples of connections and tubes described above, by way of example only, but it involves any variations that may be considered by anyone skilled in the art in the context of the appended claims.
    权利要求:
    Claims (14)
    [0001]
    1. Threaded connection (1), comprising a first and second tubular components, the first component comprising a male end comprising a distal surface and a threaded area (5) disposed on an outer peripheral surface of the male end, the second component comprising an end female comprising a distal surface and a threaded zone (4) arranged on an internal peripheral surface of the female end, the threaded zone (5) of the male end being threaded into the threaded zone (4) of the female end, the threaded zones ( 4, 5) comprising the respective male and female threads (40, 50) having a width that increases from the respective distal surface of the male and female ends, the threads comprising loading flanks (43, 53) having negative angles in at least one part of a radial dimension of the load flanks, and penetration flanks (44, 54), with a radial clearance remaining in the connected state of at least one between the crowns (51) of the male threads and the roots (42) of the female threads and / or between the crowns (41) of the female threads and the roots (52) of the male threads, with a radial gap remaining in the connected state between the flanks of penetration (44, 54) of the male and female threads, the distal surface of the male end and / or the female end being brought into contact with axial abutment against the corresponding abutment surface, characterized by the fact that the penetration flanks (44, 54 ) are at an angle in the range of 1 ° to 15 ° and the female end comprises, between its distal surface and its threaded area (6), a metal / metal sealing surface cooperating with a corresponding sealing surface provided in the male end.
    [0002]
    2. Threaded connection according to claim 1, characterized by the fact that the axial clearance between the penetration flanks (44, 54) is in the range 0.002 mm to 1 mm.
    [0003]
    Threaded connection according to claim 1 or 2, characterized by the fact that the radial clearance is provided at the roots of the threads of the male threaded zones (5).
    [0004]
    Threaded connection according to any one of claims 1 to 3, characterized in that the radial clearance is provided in the thread crown of the male threaded areas (5).
    [0005]
    Threaded connection according to any one of claims 1 to 4, characterized by the fact that the radial clearance is in the range 0.05 mm to 0.5 mm.
    [0006]
    Threaded connection according to any one of claims 1 to 5, characterized in that the load flanks (43, 53) are at an angle in the range of -1 ° to -15 °.
    [0007]
    Threaded connection according to any one of claims 1 to 6, characterized in that the penetration flanks (44, 54) are at an angle in the range of 3 ° to 5 °.
    [0008]
    Threaded connection according to any one of claims 1 to 7, characterized in that the load flanks (43, 53) are at an angle that differs from the penetration flanks (44, 54).
    [0009]
    Threaded connection according to any one of claims 1 to 8, characterized in that the distal surface of the male end is in axial abutment contact with the corresponding abutment surface of the female end.
    [0010]
    Threaded connection according to any one of claims 1 to 9, characterized in that the distal surface of the female end is in axial abutment contact with the corresponding abutment surface of the male end.
    [0011]
    Threaded connection according to any one of claims 1 to 10, characterized in that the contact surfaces (7, 8) in mutual contact are at an angle in the range of 0 ° to 45 ° with respect to a radial plane.
    [0012]
    Threaded connection according to one of claims 1 to 11, characterized in that the male end comprises, between its distal surface and its threaded area (5), a metal / metal sealing surface cooperating with the sealing surface corresponding provided on the female end.
    [0013]
    Threaded connection according to any one of claims 1 to 12, characterized in that the threaded areas (4, 5) are of the multiple entry thread type.
    [0014]
    Threaded connection according to any one of claims 1 to 13, characterized in that the threaded areas have a tapered generatrix with an inclination of 4% to 15%.
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    同族专利:
    公开号 | 公开日
    CN102639911A|2012-08-15|
    CA2781271A1|2011-05-26|
    BR112012012134A2|2016-04-12|
    MX337725B|2016-03-15|
    MY164357A|2017-12-15|
    EA201270635A1|2012-11-30|
    WO2011060894A3|2011-11-10|
    FR2952993A1|2011-05-27|
    FR2952993B1|2011-12-16|
    EP2501974B1|2016-02-17|
    AR079110A1|2011-12-28|
    EP2501974A2|2012-09-26|
    CA2781271C|2018-03-13|
    WO2011060894A2|2011-05-26|
    JP2013511672A|2013-04-04|
    CN102639911B|2016-01-06|
    EA021456B1|2015-06-30|
    PL2501974T3|2016-08-31|
    MX2012005796A|2012-06-19|
    AU2010321285A1|2012-05-24|
    UA110101C2|2015-11-25|
    AU2010321285B2|2016-11-17|
    US9273521B2|2016-03-01|
    US20130069364A1|2013-03-21|
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    法律状态:
    2016-10-25| B25A| Requested transfer of rights approved|Owner name: VALLOUREC MANNESMANN OIL AND GAS FRANCE (FR) , NIPPON STEEL CORPORATION (JP) Owner name: VALLOUREC MANNESMANN OIL AND GAS FRANCE (FR) , NIP |
    2016-11-29| B25D| Requested change of name of applicant approved|Owner name: VALLOUREC MANNESMANN OIL AND GAS FRANCE (FR) , NIP |
    2017-03-01| B25D| Requested change of name of applicant approved|Owner name: NIPPON STEEL AND SUMITOMO METAL CORPORATION (JP) , |
    2019-01-08| B06F| Objections, documents and/or translations needed after an examination request according art. 34 industrial property law|
    2019-03-19| B06T| Formal requirements before examination|
    2019-08-27| 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) |
    2020-01-28| B07A| Technical examination (opinion): publication of technical examination (opinion)|
    2020-08-25| B09A| Decision: intention to grant|
    2020-12-29| B16A| Patent or certificate of addition of invention granted|Free format text: PRAZO DE VALIDADE: 10 (DEZ) ANOS CONTADOS A PARTIR DE 29/12/2020, OBSERVADAS AS CONDICOES LEGAIS. |
    优先权:
    申请号 | 申请日 | 专利标题
    FR0905586A|FR2952993B1|2009-11-20|2009-11-20|THREADED JOINT|
    FR0905586|2009-11-20|
    PCT/EP2010/006823|WO2011060894A2|2009-11-20|2010-11-09|Threaded connection|
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