• 专利附录
  • 专利说明
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    • 专利摘要:
    threaded joint for everything. the present invention relates to a threaded joint for a pipe in which the sealing capacity, the compressive strength and the abrasion resistance are enhanced. specifically, an outer peripheral surface of the pin tip (30) forms an outward convex curve in an axial cross-sectional view; the convex curve is such that a composite curve r (n), in which a plurality of outward convex arcs with different radii of curvature (rs) are connected in sequence to a line generating a cylindrical part near a male member ( 5), it is curved such that the radii of curvature (rs) increase with the distance from the male member (5) and the tangents at the connection points of the arches are aligned with those of the corresponding arcs connected to them; and the inner peripheral surface of a housing component (1) facing the pin tip (30) is a tapered surface (20) that interferes with the outer peripheral surface of the pin tip (30) when connected to a pin component (3).
    公开号:BR112012033452B1
    申请号:R112012033452-2
    申请日:2011-06-22
    公开日:2020-09-29
    发明作者:Osamu Sonobe；Takuya Nagahama；Masaki Yoshikawa；Jun Takano；Takamasa Kawai；Kazunari Takahashi
    申请人:Jfe Steel Corporation；
    IPC主号:
    专利说明:

    TECHNICAL FIELD
    [001] The present invention relates to a threaded joint for tubes and, more specifically, a threaded joint for tubes with high sealing capacity and high resistance to compression, which is suitable for use in connecting tubes for use, generally, in the exploration of a well for oil and gas and in production, such as tubular petroleum products (OCTG), including piping and coating, risers and pipes for oil pipelines. BACKGROUND OF THE TECHNIQUE
    [002] Threaded joints are widely used in connecting tubes for use in oil and gas production, such as oil well tubes. For the connection of tubes for use in oil and gas exploration and production, standard threaded joints based on the Ameritubo Petroleum Institute (API) standard are conventionally used. However, since crude oil wells and natural gas wells have recently increased in depth, and horizontal wells and directional wells are now more common than vertical wells, excavation and production are increasingly under strict conditions. In addition, an increase in the development of the well in hostile environments, such as in the ocean and in the polar regions, has led to diverse performance requirements for threaded joints, such as compressive strength, flexural strength and resistance to external pressure. This therefore increases the use of special high performance threaded joints called premium joints.
    [003] The premium joint is usually a joint composed of a pin component and a box component joined, each of which includes a tapered thread, a seal (specifically, a metal-to-metal seal) and a shoulder (specifically, a torque rebound). The tapered thread has a key function in securely fixing the tubular joint, the seal guarantees the ability to seal due to the box component and the pin component that come into contact through the metal in this part, and the shoulder serves as a face of the bearing that acts as a support during the composition of the joint.
    [004] Figures 2 to 4 are schematic explanatory diagrams of a premium joint for an oil well pipe, which are seen in vertical cross section of a cylindrical threaded joint. The threaded joint includes a pin component 3 and a housing component 1 that corresponds to it. The pin component 1 (pin 3) has a male member 7 on its outer surface and an unthreaded part called a nozzle 8 (pin nozzle 8) at one end of pin 3, which is provided near the male member 7. Nozzle 8 has a seal 11 on its outer peripheral surface and a torque shoulder 12 on its end face. The opposite housing component 1 has a female member 5, a seal 13 and a shoulder 14 on the inner surface, which are parts that can be screwed onto the male member 7, the seal 11 and the shoulder 12 of pin 3 or come into contact with these, respectively.
    [005] Examples of the related technique of the previous premium joint are revealed in Patent Literature 1 to 6. CITATION LIST PTL 1 PATENT LITERATURE: Japanese Patent No. 4535064 PTL 2: Japanese Patent No. 4208192 PTL 3: Publication of Order Japanese Examined Utility Model Registration Number No. 61-44068 PTL 4: Japanese Patent No. 4300187 PTL 5: Japanese Unexamined Patent Application Publication No. 2001-124253 PTL 6: Japanese Patent No. 2705506 SUMMARY OF THE INVENTION TECHNICAL PROBLEM
    [006] In the example of figures 2 to 4, the metal-to-metal seal is provided at one end of the pin nozzle 8. However, Patent Literature 1 proposes a threaded gasket in which a metal to metal seal is provided. on a part of the pin nozzle 8 near the threaded part, and the nozzle extends along the seal to the shoulder to increase resistance to external pressure. The threaded joint disclosed in Patent Literature 1 is configured such that the pin tip, which is not in contact with the housing component, extends longitudinally to be discontinuous from the seal and to avoid reducing the pin tip thickness, to achieve the intensification not only of the external pressure resistance described above, but also of the axial compression resistance.
    [007] Patent Literature 2 describes the provision of a portion that has a discontinuous shape for the seal, called an appendix, from the seal to an end of the pin tip to ensure radial stiffness and decrease axial stiffness to deform the appendix during composition and to intensify the resistance to tension due to its recovery under extensible load.
    [008] As described in Patent Literature 1 and 2, placing the seal near the threaded part of the pin to separate it from the tip end of the pin is efficient in intensifying the resistance to external pressure and the resistance to tension and in supplying the stable performance for the thread, which can also be confirmed by the FEM simulation or similar, in addition, the discontinuous pin nozzle for the seal is deformed in itself when strong axial compression is exerted on it, which also offers the effect to reduce the plastic deformation of the torque relief of the box component. However, on the other hand, the pin tip is likely to be deformed inappropriately, which may depend on the composition torque.
    [009] Since the composition torque is influenced by the lubrication condition, the surface properties, etc., a radial sealing method is proposed as a project that does not depend on it to a large extent, in which the radial component of the contact pressure of the seal is relatively increased. For example, Patent Literature 3 discloses an example of a radial seal method in which the pin seal has a large R shape and a small tapered seal angle. However, a problem with such a radial sealing method in which the tapered sealing angle is small is that abrasion is prone to occur during composition. In particular, in the event that a large amount of sealing interference is required to ensure the sealing ability and stability of the sealing, the susceptibility to the occurrence of abrasion is further increased.
    [0010] To solve the above problems, Patent Literature 4 increases a contact area of the seal to reduce the contact pressure when defining the large radius of a toroidal sealing surface. This measure is thus effective, notably reducing the tendency of abrasion of the metal-to-metal seal. However, there is a problem in the case where the contact pressure decreases due to small disturbances, because the large R decreases the contact pressure, thus producing an insignificant leakage path in the metal-to-metal seal and, this leakage is not easy to fix. Furthermore, it is physically difficult to separate the metal-to-metal seal from the tip end because of the large R and thus ensuring the distance between the metal-to-metal seal and the pin tip to a certain extent or even longer results in an excessively small thickness of the tip end of the pin.
    [0011] As for the performance of axial compression, it is efficient to reduce a lateral gap in the flank of the thread penetration, as described in Patent Literature 5 or 6. However, if the gap is very small, abrasion is likely to occur in the thread and then an appropriate gap is needed.
    [0012] The threaded joints proposed in the related art still have some problems as described above, and then there is room for further refinement to satisfy a variety of performance requirements for compressive strength, flexural strength, pressure sealing capability external, etc. of the threaded joints described above. Accordingly, it is an object of the present invention to provide a threaded joint for a tube that is enhanced in terms of sealing ability, compressive strength and abrasion resistance in view of such circumstances. SOLUTION TO THE PROBLEM
    [0013] The inventor and the associated person made the present invention with the following context and configuration with careful examination to find ways to solve the above problems. That is, the present invention is as follows: (1) A threaded joint for a tube, comprising: a pin component that includes a male member, a nozzle that extends to an end of the tube from the male member and a shoulder provided at one end of the nozzle; and a housing component that includes a female member screwed into the male member, an inner peripheral surface facing the outer peripheral surface of the pin component nozzle and a shoulder that makes contact with the shoulder of the pin component, where the pin and housing component are connected by the screw connection so that the outer peripheral surface of the pin component nozzle and the inner peripheral surface of the housing component between metal-to-metal contact so that the contact interface forms a sealing surface , where the outer peripheral surface of the pin component nozzle forms an outward convex curve in the axial cross-sectional view of the pin component, and the convex curve is such that a composite R curve, in which a plurality of convex arcs for outside having different radii of curvature, Rs, are connected in sequence to a generating line of a cylindrical part close to the male member, it is curved as and the radii of curvature, Rs, of the arcs increase with the distance from the male member and the tangents at the connection points of the arcs are aligned with those of the corresponding arcs connected to them; and the inner peripheral surface of the box component is a tapered surface that interfaces with the outer peripheral surface of the pin component nozzle when connected with the pin component. (2) Threaded joint for a pipe, according to (1), in which the angles that the individual arcs in the compound R curve form increase with decreasing distance from the male member. (3) The threaded joint for a pipe, according to (1) or (2), in which any of the connection points on the composite R curve serve as a starting point of contact with the tapered surface. (4) The threaded joint for a pipe, according to any one of (1) to (3), in which an angle that the tapered surface forms with respect to the axial direction of the joint is within ten degrees. (5) The threaded joint for a tube, according to any one of (1) to (4), in which the tip of the pin component is 20 mm or more in length. (6) The threaded joint for a tube, according to any one of (1) to (5), in which the angles of the penetration flank of the male and female members are within the range of zero degrees to 30 degrees. (7) The threaded joint for a pipe, according to any one of (1) to (6), in which the load flange angles of the male and female members are within the range of -5 degrees to four degrees . (8) The threaded joint for a pipe, according to any one of (1) to (7), in which the boss angle of the boss is within the range of zero degrees to 20 degrees. (9) The threaded joint for a pipe, according to any one of (1) to (8), in which the thread gap between the male member and the female member is within the range of 0.01 mm to 0, 1 mm. (10) A threaded joint for a pipe, in which the composite curve R in which a plurality of arcs having different radii of curvature, Rs, are connected in sequence to the generating line of the cylindrical part near the male member in either ( 1) to (9) is replaced by a composite curve R in which a plurality of arcs with different radii of curvature, Rs, are connected in sequence to the generating line of the cylindrical part near the male member directly or through the segments of the line that have a length of 2.5 mm or less. (11) A threaded joint for a tube, in which the composite curve R in which a plurality of arcs having different radii of curvature, Rs, are connected in sequence to the generating line of the cylindrical part near the male member in either ( 1) to (9) is replaced by a composite curve R in which a plurality of arcs with different radii of curvature, Rs, are connected in sequence to the generating line of the cylindrical part close to the male member directly or by means of a arc with a length of 2.5 mm or less and a radius of 250 mm or more and three times or more the radius of an adjacent arc. ADVANTAGE EFFECTS OF THE INVENTION
    [0014] The present invention can provide a threaded joint for a tube in which the sealing capacity, the compressive strength and the abrasion resistance are enhanced. BRIEF DESCRIPTION OF THE DRAWINGS
    [0015] Figure 1 (a) is a component of pin 3 of the cross-sectional view showing a nozzle of a threaded joint for a tube according to an embodiment of the present invention.
    [0016] Figure 1 (b) is a box component 1 of the cross-sectional view showing a nozzle of a threaded joint for a tube according to an embodiment of the present invention.
    [0017] Figure 1 (c) shows a state in which the pin component 3 and the housing component 1 are joined from the cross-sectional view showing a nozzle of a threaded joint for a pipe according to one embodiment of the present invention.
    [0018] Figure 2 is a cross-sectional view showing a conventional threaded joint for a pipe.
    [0019] Figure 3 is seen in an enlarged cross section showing the vicinity of a pin tip in Figure 2.
    [0020] Figure 4 is an enlarged cross-sectional view showing a threaded part in Figure 2.
    [0021] Figure 5 is a cross-sectional view showing the definitions of a threaded gap, a load flank angle and a penetration flank angle.
    [0022] Figure 6 is a figure showing a load schedule in a leak test simulation. DESCRIPTION OF THE MODALITIES
    [0023] As described above, providing the seal in a position away from the tip of the nozzle to extend the seal nozzle to the boss is efficient in enhancing the external pressure resistance and the resistance to tension and the supply of the thread with stable performance. Thus, the inventor and an associate have considered the shape around the seal to separate the seal from the tip end (or shoulder) and to prevent the thickness of the tip end from becoming too small.
    [0024] As a result, the concept that the external peripheral surface of the pin component nozzle forms an outward convex curve in the axial cross-sectional view of the pin component has been outlined; the inner peripheral surface of the box component facing the outer peripheral surface of the pin component nozzle is a tapered surface that intersects the convex curve of the pin component at two points in axial cross-sectional view of the box component; the outer peripheral surface of the pin component nozzle and the inner peripheral surface (hereinafter also referred to as a tapered surface) of the housing component facing the outer peripheral surface of the nozzle forms a metal-to-metal seal; and in the case where the side interfaces of the pin component and the side interface of the seal housing component serve as the sealing surfaces of the components, the convex curve of the pin component is such that a composite R curve, in which a plurality of arcs with different radii of curvature, Rs, are connected in sequence to a generating line of a cylindrical part close to the male member, it is curved such that the radii of curvature, Rs, of the arcs increase with the distance from the male member and the tangents at the connection points of the arcs are aligned with those of the corresponding arcs connected to them; and thus, the seal can be detached from the tip end without decreasing the thickness of the tip end of the pin.
    [0025] Figure 1 (a), figure 1 (b) and figure 1 (c) are a cross-sectional view showing a nozzle of a threaded joint for a pipe according to an embodiment of the present invention, where ( a) shows a pin component 3, (b) shows a box component 1 and (c) shows a state in which the pin component 3 and the box component 1 are joined. The pin component 3 is provided at one end of a tube and includes a male member 7, a nozzle 8 that continues to the side of the tube from the male member 7 and a torque shoulder 12 provided at one end of the nozzle 8. On the other hand, the housing component 1 includes a female member 5 screwed to the male member 7 of the pin component 3, a tapered surface 20 which is the inner peripheral surface of the housing component 1 facing the outer peripheral surface of the nozzle 8 ( external peripheral surface of the nozzle 30) in the state in which the pin component 3 and the housing component 1 are joined by the screw connection, and a shoulder 14 that contacts the shoulder 12.
    [0026] The outer peripheral surface of the nozzle 30 has an external convex curve in the axial cross-sectional view of the pin component 3. On the other hand, the inner peripheral surface of the box component 1 facing the outer peripheral surface of the nozzle 30 forms a tapered surface 20 (tapered surface) provided with a fixed inclination (referred to as a tapered angle) α with respect to the axial direction of the threaded joint. When the pin component 3 and the housing component 1 are joined, the tapered surface 20 and the outer peripheral surface of the nozzle 30 interfere with each other to form a seal 40. The taper angle α is defined so that the convex curve and the tapered surface generating line 20 intersects at the two points in the axial cross-section view of the threaded joint in an imaginary composition stage without interference between the pin component 3 and the housing component 1, and the seal 40 is, in fact, formed in a strip (interference area 40a) between the two points of intersection.
    [0027] The convex curve formed along the outer peripheral surface of the nozzle 30 will be described using the composite R curve consisting of three arcs shown in figure 1 (a). This curve is a composite R curve N in which the arcs Ni, N2 and N3 which have different radii of curvature, Ri, R2 and R3, are connected in sequence to a segment of the line No which is a generating line of a nearby cylindrical part of the male member 7. This composite R curve N has a curved shape in which the radii of curvature of the arcs increase with the distance from the male member 7, that is, RI <R2 <R3. This allows the thickness of the shoulder 12 (thickness of the shoulder) t at the tip end of pin 8 to be increased. For comparison, figure 1 (c) shows, in a broken line, a case in which the convex curve is a single RM curve (a single arc with a radius of curvature, R) and the interference area of its seal is equal to the interference area 40a of the seal 40 of the composite R curve N. This shows that, with such a single RM curve, the shoulder thickness is smaller compared to the case of the composite R curve N. The small shoulder thickness causes insufficient stiffness of the tip of the pin 8, 0 which prevents the pressure of the seal contact 40 from being properly guaranteed. In contrast, an attempt to ensure sufficient shoulder thickness with a single R curve causes seal 40 to be distant from male member 7.0, which is undesirable from the point of view of ensuring sufficient resistance to external pressure and resistance to tension.
    [0028] The composite R curve N has a curved shape such that a tangent at a connection point of an arc and that of a connected arc are aligned with each other. For example, at a connection point between the arcs Ni, N2 and N3 and at a connection point between the arcs N2 and N3, the tangents of the arcs that are connected together are aligned with each other. In this way, the convex curve is shaped into a continuous curve in which no point of retraction is present, which reduces improper nozzle deformation. The arcs to be connected can be directly connected, or alternatively, connected via a line segment aligned with a tangent common to the arcs or an arc with a sufficient radius (a radius of 250 mm or more and three times or more than that adjacent arc) to 0 for which there is no need to consider changes in angle. To ensure that contact pressure under which no leakage path is formed, it is preferable to determine the length of the line segment or an arc with a sufficient radius described above as 2.5 mm or less.
    [0029] At present, it is preferable that the angles θi, 62 and 03 that the arcs Ni, N2 and N3 form, respectively, increase with the decreasing distance from the male member 7, that is, θi> 02> 03. otherwise, it is difficult to project the composite R curve at a limited length of the tip 8 of the pin component 3 (0 length L of the pin tip in figure 1 (a)) or a limited length of the interference area 40a (referred to as a contact length of the seal).
    [0030] Furthermore, it is preferable that any of the connection points on the composite R curve, for example, a connection point between the Ni and N2 arcs, and a connection point between the N2 and N3 arcs, is aligned with a point contact starting point that indicates a point at which the composite R curve first contacts the tapered surface 20 of the box component 1. When defining any of the arc connection points on the composite R curve as the starting point of contact, a part that has a large R, a low contact pressure and a long contact length and a part that has a small R, a high contact pressure and a short contact length are formed in the contact pressure distribution of the sealing, thereby reducing the tendency to produce a leak path, thereby intensifying the sealing capacity.
    [0031] However, in practice, it is sometimes difficult to fully align the contact point of the arcs with the starting point of contact with the tapered surface of the box component because of the manufacturing tolerance of a thread cutting device . In this case, the slope of a tangent at the arc connection point can be set less than the slope of the tapered surface of the box component by a maximum of 0.5 degrees. In the real composition, a deformation such that the end of the pin tapers occurs due to the radial interference of the pin and the box, which makes the inclination of a tangent to the surface of the pin at the conclusion of the composition greater than a projected value.
    [0032] Therefore, determining the slope of a tangent at the arc contact point to a value less than the cone slope of box component 1 by 0.5 degrees or less has substantially the same effect as when the slopes match .
    [0033] It is preferable that the distance between the starting point of contact and the end of the male member, x, (see figure 1 (c)) is less than 0.7L (Léo length of the pin tip, as described above ) from the point of view of separating the seal from the end of the nozzle, and if the distance between the starting point of contact and the end of the male member is less than 0.2L, interference between the seal and the thread is prone to occur and then it is preferable to be 0.2L or more. To ensure safety, it is preferable to be 0.3 L or more.
    [0034] It is preferable that the taper angle α of the tapered surface 20 of the box component 1 is within ten degrees. By defining the taper angle α (see figure 1 (b)) within ten degrees, and more preferably, within five degrees, the radial sealing method can be achieved appropriately and then the torque dependence of the composition on the sealing capacity is relatively diminished.
    [0035] It is preferable that the length L of the pin tip (see figure 1 (c)) is 20 mm or more. This can sufficiently separate the seal from the tip end of the pin, and as a result, can significantly reduce damage to the seal due to elastic deformation in the range of the separation distance, thus offering the effect of stabilizing the capacity sealing.
    [0036] The stabilized sealing capacity allows a quantity of S interference seal (see figure 1 (c)) to be relatively small for the radial sealing method, thus reducing the tendency to abrasion.
    [0037] Of the two or more Rs in the composite R curve, a relatively small R is preferably defined at 2.54 cm (one inch) or less, a relatively large R is more preferably determined at 5 cm (two inches) or more, and an even greater R is preferably determined to be 7.6 cm (three inches) or more. More specifically, at least one of the plurality of Rs of the composite R curve is preferably defined as 5 cm (two inches) or more (more preferably, 7.6 cm (three inches) or more), and the remaining Rs are preferably determined as less than 5 cm (two inches) (more preferably, 2.54 cm (one inch) or less). When determining at least one of the plurality of Rs of the R curve composed preferably as 5 cm (two inches) or more (more preferably, 7.6 cm (three inches) or more), the contact length of the seal may be easily guaranteed, and by determining the remaining Rs preferably less than 5 cm (two inches) (more preferably, 2.54 cm (one inch) or less), high contact pressure can be easily achieved.
    [0038] The number of arcs in the composite R curve (the number of arcs that have different Rs) can be two or more shown in figure 1 (a) or, alternatively, four or more. Although the increase in the number of arcs increases the length of the seal contact, thus facilitating the intensification of the sealing capacity, the number of arcs can be designed according to the performance actually required for the threaded joint because the load and the Actual production work, such as size checking, increases.
    [0039] Furthermore, it is preferable to determine the cross-sectional area of the pin component at the starting point of contact for 35% or greater of the cross-sectional area of the main body of a pipe at the end of which the joint is formed (the area cross section of an unprocessed pin part). By defining such an area in cross section of the pin, the rigidity of the pin component at the starting point of contact is increased and, in particular, resistance to high external pressure is easily obtained. Preferably, the cross-sectional area of the pin component at the starting point of contact is determined to be 40% or more of the cross-sectional area of the main body of the pipe.
    [0040] It was confirmed that defining one or two or more of the load flank angle, the penetration flank angle and the thread gap of the male and female members in the desirable ranges, in addition to limiting the shape around the sealing, described above, enhances the overall sealing ability due to the effect of the combination. At present, the loading flank angle is a loading flank angle β shown in figure 5, that is, an angle β that a loading flank surface 18 forms with an orthogonal surface of the geometric axis of the thread (an orthogonal surface the axial direction of the threaded joint, also for the following). The penetration flank angle is a penetration flank angle y shown in figure 5, that is, an angle y that a penetration flank surface 19 forms with the orthogonal surface of the geometric axis of the thread. The thread gap is a gap G shown in figure 5, that is, the gap G between a thread edge 7a of the male member and a groove of the thread 5a of the female member that engages between them.
    [0041] The optimal variation of the load flank angle β is from -5 degrees to four degrees. The lower limit of the optimal variation is determined from the point of view of abrasion resistance and the life of the thread tool, and the surface limit is determined from the point of view of bending strength.
    [0042] The optimal variation of the penetration flank angle y is from zero degrees to 30 degrees. The lower limit of the optimal variation is determined from the point of view of abrasion resistance, tool life and performance of the thread composition, and the upper limit is determined from the point of view of axial compression strength. .
    [0043] The optimal variation of the G thread gap is 0.01 to 0.1 mm. The lower limit is determined from the point of view of reducing the tendency to excoriation and the upper limit is determined from the point of view of reducing the load at the end of the pin under axial compression load. The gap of the G thread is preferably at least about 0.03 mm in consideration of an error induced during threading. Due to the realization that the G-thread gap of about 0.045 mm provides sufficient performance, it can be about 0.045 mm depending on the circumstances.
    [0044] The general intensification effects of the sealing capacity, due to the determination of one or two or more of the load flank angle, the penetration flank angle and the thread gap, as described above, are eminent particularly in the condition that the axial tension + the internal pressure or the external pressure, once the axial compression is exerted, are loaded.
    [0045] The boss angle of the boss (an angle that the face of the boss end in the axial direction of the joint forms with an orthogonal surface of the joint's geometric axis, which is assumed to be a positive angle in the case where the side of the joint outer periphery of the interface pin protrudes outwardly from the side of the inner periphery of the pin) is preferably zero to 20 degrees. A rebound angle of less than zero degrees is unfavorable for the sealing ability and characteristics of the composition. On the other hand, a shoulder angle of more than 20 degrees is unfavorable because the plastic deformation of the housing shoulder and the local deformation of the seal tend to occur. Preferably, it is 15 degrees or less. In addition, it is preferably seven degrees or less depending on the circumstances. EXAMPLES
    [0046] An evaluation was made of a threaded joint for a tube according to the present invention shown in figure 1 or in which two of the arcs of the curve R composed in figure 1 (a) are connected by a line segment. Tables 1 and 2 show the sizes, formats and results of the evaluation of the examples of the present invention and the comparative examples. All the components of the pin were formed at the ends of the tubes with an external diameter of 244.48 mm and a wall thickness of 13.84 mm. The threads have 5 TPI (five threads by 2.54 cm - 1 inch). A leak test based on ISSO 13679: 2002 was simulated as an evaluation by FEM analysis, in which the contact pressure area (psi-inch) of the seal was evaluated. The contact pressure area is obtained by integrating the contact pressure with the seal contact area. This leak test is a load test on a threaded joint for a pipe based on a biaxial stress that corresponds to 95% of the material yield conditions, an internal pressure, a lower biaxial stress that corresponds to the collapse conditions described in the ISSO 10400: 2007 and a biaxial tension that corresponds to 95% of the material's yield conditions, and an external pressure, which were imposed in the programming shown in figure 6.
    [0047] As an index that indicates the tendency to excoriation during composition, an index of excoriation (psi inch) = pressure by contact x sliding distance was obtained by the FEM analysis, which is defined by the product of sliding distances (distances of slip) (inch) and contact pressures (psi) at the individual axial positions of the seal from the beginning of the composition to the end. This is also achieved by integration. In general, the lower the excoriation index, the lower the tendency to excoriation.
    [0048] For comparison purposes, the contact pressure areas and excoriation indices were determined for: • Comparative Examples 1, 3, 4: The generating line of the outer peripheral surface of the pin 8 nozzle is shaped like a curve convex endowed with a single R (the only RM curve indicated by the broken line in figure 1 (c)). • Comparative Example 2: The generating line of the outer peripheral surface of the pin 8 tip is a composite R curve, but the requirement that the arcs' Rs increase with the distance from the male member 7 is not satisfied.
    [0049] Furthermore, for these examples of the present invention and the comparative examples, a plurality of samples with different amounts of interference in the seal, with an amount of thread interference of 0.305 mm per diameter, was prepared, and a physical test was conducted using a test method specified by ISSO 13679: 2002. In addition, a plurality of samples with different amounts of interference in the seal, with an amount of thread interference of 0.127 mm per diameter, was prepared, and a composition test repeated 13 times so 13. the amount of interference on the minimum seal at which no leakage occurred in the physical test and the amount of interference on the maximum seal at which no abrasion occurred during the 13 times of the composition in the repeated composition test were determined by the tests, and the difference between them was determined to be a variation in the amount of interference in the configurable seal.
    [0050] Tables 1 and 2 show, in addition to the sizes of the individual components of the threaded joints, the pressure areas and excoriation indexes obtained by the FEM calculation and the amounts of interference in the maximum and minimum seal determined by the actual physical test and the repeated composition test. At present, the amounts of interference in the seal in Tables 1 and 2 are values per diameter, which correspond to the amount of interference in the Sx 2 seal, shown in figure 1 (c). The contact pressure areas in the internal pressure condition in the FEM calculation in all examples were the minimum values (which correspond to a state in which leakage is more likely to occur) in the vicinity of the loading steps L3 and L18 (loading effort). biaxial tension + internal pressure) in the programming in figure 6. Although the load point is not specified in ISSO 13679, it is the most severe condition for internal pressure + tension conditions and is sometimes necessary and, therefore, was used at present for comparison.
    [0051] On the other hand, the contact pressure areas under the conditions of external pressure in the FEM calculation in all examples were the minimum values in the vicinity of a load step L15 (biaxial stress effort + external pressure) in the programming in the figure 6. Tables 1 and 2 show the minimum values of the contact pressure areas in the individual examples with relative minimum values. At present, the internal pressure is charged with gas and the external pressure is charged with water, and then the susceptibility to leakage differs; therefore, the minimum relative values were obtained with reference to the respective minimum values in the condition of internal pressure and in the condition of external pressure. Specifically, for the minimum value in L3 and L18 the lowest minimum value in all examples for L3 and L18 was determined at 100, and others were expressed as reasons for them. For the minimum value in L15, the lowest minimum value in all examples for L15 was set to 100, and the others were expressed as reasons for them.
    [0052] The loading stage L18, after compression hysteresis was once subjected, exhibited a lower sealing capacity than the sealing capacity in the L3 loading stage, which is the same point of the loading as that before the compression hysteresis is subjected, which is insignificant, in particular, in Comparative Example 3, in which there is not enough shoulder thickness. In all results, the examples of the present invention exhibited good sealing ability at L18 after being subjected to compression hysteresis.
    [0053] As for the excoriation index, an axial position of the joint in which the maximum value (which corresponds to a state in which the tendency to excoriation is the highest) differed from example to example. Tables 1 and 2 show the maximum values of the excoriation indexes of the individual examples as relative maximum values (the maximum value in all examples is set to 100 and the others are expressed as reasons for it).
    [0054] Table 3 shows the results of the evaluation with other sizes. The materials of the object have an external diameter of 139.7 mm, a wall thickness of 7.72 mm and 5 TPI and have an external diameter of 346.08 mm, a thickness of 15.88 mm and 4 TPI. The examples of the present invention exhibited good sealing ability after being subjected to compression hysteresis and high excoriation performance during composition with all sizes.
    [0055] The results of the evaluation shown in Tables 1, 2 and 3 show that the examples of the present invention reached the threaded joints with excoriation indices less than or equal to those of the comparative examples and with variations in the amount of interference of wide configurable seal , wide and high sealing capacity and abrasion resistance, even though the contact pressure areas (pressure contact areas) were higher. Table 1


    Table 2


    Table 3

    REFERENCE LISTING 1 box component 3 pin (pin component) 5 female member (female member) 5th female member thread groove 7 male member (male member) 7th male member thread edge 8 nozzle (pin tip) 11 , 13, 40 seal (specifically, metal-to-metal seal) 12, 14 shoulder (specifically, torque shoulder) 18 load flank surface 19 penetration flank surface 20 inner peripheral surface (tapered surface) of the opposite housing component to the outer peripheral surface of the pin component nozzle 30 outer peripheral surface of the pin component nozzle (outer peripheral surface of the pin nozzle) 40th interference area
    权利要求:
    Claims (11)
    [0001]
    1. Threaded joint for a tube, comprising: a pin component (3) that includes a male member (7), a nozzle (8) that extends to an end of the tube from the male member (7), and a shoulder (12) provided at one end of the nozzle (8); and a housing component (1) that includes a female member (5) screwed to the male member (7), an inner peripheral surface (20) facing the outer peripheral surface (30) of the nozzle (8) of the pin component ( 3) and a shoulder (14) that contacts the shoulder (12) of the pin component (3), where the pin component (3) and the housing component (1) are connected by the screw connection to that the outer peripheral surface (30) of the pin component nozzle (3) and the inner peripheral surface (20) of the housing component (1) come into metal-to-metal contact so that the contact interface forms a sealing surface , characterized by the fact that: the outer peripheral surface (30) of the pin component nozzle (3) forms an outward convex curve in the axial cross-sectional view of the pin component, and the convex curve is such that an R curve compound, in which a plurality of outward convex arcs have different radii of curvature, Rs, are cone connected in sequence to a generator line of a cylindrical part close to the male member (7), it is curved such that the radii of curvature, Rs, of the arcs increase with the distance from the male member (7) and the tangents at the points of connection arcs are aligned with those of the corresponding arcs connected to them; and the inner peripheral surface (20) of the housing component (1) is a tapered surface that interferes with the outer peripheral surface (30) of the pin component nozzle (3) when connected to the pin component (3).
    [0002]
    2. Threaded joint for a tube, according to claim 1, characterized by the fact that the angles that the individual arcs in the composite R curve form increase with the de-increasing distance from the male member (7) .
    [0003]
    3. Threaded joint for a pipe according to claim 1 or 2, characterized by the fact that any of the connection points on the composite R curve serve as a starting point for contact with the tapered surface.
    [0004]
    Threaded joint for a pipe according to any one of claims 1 to 3, characterized by the fact that an angle that the tapered surface forms with the axial direction of the joint is within ten degrees.
    [0005]
    Threaded joint for a pipe according to any one of claims 1 to 4, characterized in that the nozzle (8) of the pin component (3) has a length of 20 mm or more.
    [0006]
    Threaded joint for a pipe according to any one of claims 1 to 5, characterized in that the penetration flank angles (y) of the male member (7) and the female member (5) are within the range of zero degree to 30 degrees.
    [0007]
    Threaded joint for a pipe according to any one of claims 1 to 6, characterized in that the loading flank angles (β) of the male member (7) and the female member (5) are within the range from -5 degrees to four degrees.
    [0008]
    Threaded joint for a pipe according to any one of claims 1 to 7, characterized by the fact that a cam shoulder angle is within the range of zero degrees to 20 degrees.
    [0009]
    9. Threaded joint for a pipe according to any one of claims 1 to 8, characterized by the fact that the thread gap between the male member (7) and the female member (5) is within the range of 0.01 to 0.1 mm.
    [0010]
    10. Threaded joint for a tube, characterized by the fact that the composite curve R in which a plurality of arcs having different radii of curvature, Rs, are connected in sequence to the generating line of the cylindrical part near the male member, as defined in any one of claims 1 to 9, is replaced by a composite curve R in which a plurality of arcs having different radii of curvature, Rs, are connected in sequence to the generating line of the cylindrical part near the male member (7) directly or by line segments that are 2.5 mm or less in length.
    [0011]
    11. Threaded joint for a tube, characterized by the fact that the composite curve R in which a plurality of arcs having different radii of curvature, Rs, are connected in sequence to the generating line of the cylindrical part near the male member, as defined in any one of claims 1 to 9, is replaced by a composite curve R in which a plurality of arcs having different radii of curvature, Rs, are connected in sequence to the generating line of the cylindrical part near the male member (7) directly or by middle of an arc having a length of 2.5 mm or less and a radius of 250 mm or more and three times or more the radius of an adjacent arc.
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    同族专利:
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    JP4930647B1|2012-05-16|
    EP3196524A1|2017-07-26|
    MX2012014880A|2013-01-24|
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    US20130181442A1|2013-07-18|
    CA2801204C|2016-08-09|
    SA3409B1|2014-05-21|
    JP2012149760A|2012-08-09|
    CN202469289U|2012-10-03|
    EP2589846A1|2013-05-08|
    RU2522756C1|2014-07-20|
    AR081782A1|2012-10-17|
    EP2589846B1|2017-06-14|
    CA2801204A1|2012-01-05|
    EP3196524B1|2021-06-09|
    AU2011272607A1|2012-12-20|
    CN102313085B|2015-10-14|
    MY156120A|2016-01-15|
    AU2011272607B2|2015-03-12|
    EP2589846A4|2015-04-01|
    BR112012033452A2|2016-12-13|
    WO2012002409A1|2012-01-05|
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    法律状态:
    2018-12-26| B06F| Objections, documents and/or translations needed after an examination request according [chapter 6.6 patent gazette]|
    2019-04-30| B06T| Formal requirements before examination [chapter 6.20 patent gazette]|
    2020-05-05| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|
    2020-09-29| B16A| Patent or certificate of addition of invention granted|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 22/06/2011, OBSERVADAS AS CONDICOES LEGAIS. |
    优先权:
    申请号 | 申请日 | 专利标题
    JP2010149547|2010-06-30|
    JP2010-149547|2010-06-30|
    JP2010289785|2010-12-27|
    JP2010-289785|2010-12-27|
    JP2011-101329|2011-04-28|
    JP2011101329A|JP4930647B1|2010-06-30|2011-04-28|Threaded joints for pipes|
    PCT/JP2011/064862|WO2012002409A1|2010-06-30|2011-06-22|Pipe screw coupling|
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