Classifications

• • E—FIXED CONSTRUCTIONS
  • E21—EARTH OR ROCK DRILLING; MINING
  • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
  • E21B17/00—Drilling rods or pipes; Flexible drill strings; Kellies; Drill collars; Sucker rods; Cables; Casings; Tubings
  • E21B17/02—Couplings; joints
  • E21B17/04—Couplings; joints between rod or the like and bit or between rod and rod or the like
  • E21B17/042—Threaded
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
  • F16L15/00—Screw-threaded joints; Forms of screw-threads for such joints
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
  • F16L15/00—Screw-threaded joints; Forms of screw-threads for such joints
  • F16L15/001—Screw-threaded joints; Forms of screw-threads for such joints with conical threads
  • F16L15/004—Screw-threaded joints; Forms of screw-threads for such joints with conical threads with axial sealings having at least one plastically deformable sealing surface
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
  • F16L15/00—Screw-threaded joints; Forms of screw-threads for such joints
  • F16L15/06—Screw-threaded joints; Forms of screw-threads for such joints characterised by the shape of the screw-thread

Definitions

• the invention relates to tubular threaded joints called upper (or “premium”) comprising at least one set of metal-metal sealing surfaces and screwing stops on the male and female threaded elements which make up the threaded joint, the threaded elements being made at the end of a tubular component of the long or short tube type (sleeve).
• tubular threaded joints are known, used in particular to constitute columns of casing or production tubes or drill pipe strings for oil wells or for similar wells, such as, for example, wells for geothermal energy.
• Such tubular threaded joints are subjected to various overall stresses (axial traction or compression, interior or exterior fluid pressure, bending, torsion), possibly combined (for example axial traction + interior pressure), of possibly fluctuating intensity.
• the upper tubular threaded joints must not only resist breakage but also remain leak-tight, in particular against gases, despite such stresses possibly combined and despite harsh conditions of use on site.
• the stresses can possibly change in nature during the descent of the tubes into the well or the exploitation, the tensile stresses can for example evolve momentarily in compression stresses.
• the threaded joints must also be able to be screwed and unscrewed several times without degrading their performance, in particular by seizing. After unscrewing, the tubular components can be reused in other wells under other service conditions.
• tubular threaded joints according to patents FR 1489013, EP 488912 and US 4494777 have a front axial abutment surface at the free end of at least one of the threaded elements, generally the male element, and a sealing surface on a peripheral surface. of a threaded element immediately adjacent to the front surface of the same threaded element.
• the part of the threaded element between the first thread of the thread and the front surface of the axial stop at the free end is generally designated by the name of lip.
• the male sealing surface is located at the end of the male lip, which is more or less long depending on the threaded joints.
• the corresponding male and female sealing surfaces then exhibit radial interference generating a contact pressure and the so-called "carrier" thread flanks located on the thread on the side opposite the free end of the threaded element are in contact under contact pressure, thus putting the lip under axial compression.
• Interference seals may cause seizure problems during tightening if their geometry is unsuitable. They can also pose risks of leakage in service if the contact pressure and in particular the integrated contact pressure over the active width of the sealing surfaces is insufficient.
• the integrated contact pressure must remain above a certain value expressed in N / mm; this integrated contact pressure is a function for a given geometry of the relative positioning of the elements at the end of screwing and of the stresses in service.
• the tensile force can come from axial tension or bending stresses.
• the threaded joint according to the invention firstly comprises, in a known manner, a male threaded element at the end of a first tubular component and a female threaded element at the end of a second tubular component.
• the male threaded element comprises a male thread, at least one male sealing surface on its outer peripheral surface and at least one male surface of axial stop.
• the female threaded element correspondingly comprises a female thread, at least one female sealing surface on its inner peripheral surface and at least one female surface of axial stop.
• the male thread is screwed into the female thread until at least one male axial abutment surface cooperates in abutment, forming a reaction to the screwing torque with the corresponding female axial abutment surface, each male sealing surface then interfering with the corresponding female sealing surface.
• an abutment surface in abutment reaction among the abutment surface (s) is formed on the free end front surface of the threaded element and is said to be a distal axial abutment surface.
• a lip separates the distal axial abutment surface from the thread on the threaded element in question, a sealing surface called “sealing surface on lip” being disposed on this lip at a given axial distance from the end of the thread.
• the lip is therefore subjected to axial compression forces resulting from the abutment in abutment reaction of the distal axial abutment surface with the corresponding axial abutment surface.
• the lip comprises a part called “appendage” between the sealing surface on the lip and the distal axial abutment surface at the free end of the lip.
• This appendage makes it possible to give the lip both a strong radial stiffness and a low axial stiffness.
• the free end front surface is a stop surface in reaction to a stop at the tightening torque and the appendix does not exercise the same set of functionalities.
• the appendix according to Fugerson (US 4624488) makes it possible to protect the bearing of marks resulting from blows during handling on site and to increase the mechanical resistance to rupture of the threaded joint by axial traction.
• the appendix according to Tung (US 4795200) also makes it possible to increase the radial stiffness of the lip on a threaded joint without distal axial abutment surface and thereby increase the contact pressure at the sealing surfaces on this threaded joint.
• the appendage according to the present invention also increased the radial stiffness of the lip on a tubular threaded joint with distal axial abutment surface and that this increase in stiffness was reflected on the upper tubular threaded joint by an increase in the effective axial contact width of the sealing surface on the lip and the integrated contact pressure over this distal width of the axial stop.
• the inventors have also found that, in a non-obvious manner, the increase in radial stiffness due to the appendage was also reflected on the upper tubular threaded joint according to the invention by an increase in the radial width of effective contact of the distal surface. axial stop as well as the integrated contact pressure over the radial width of this distal axial stop surface.
• the appendix reduces the axial stiffness of the lip and consequently increases the elastic deformation of the lip at constant axial compression stress. This increased elastic deformation allows when a tensile load is exerted on the threaded joint to offset the detachment of the stop and especially the critical value of contact pressure integrated over the width of the sealing surface on the lip towards relatively high values. tensile load.
• the appendage can be bordered by any peripheral surface but a substantially cylindrical peripheral surface is preferred so as to maximize the radial thickness of the distal axial abutment surface.
• the axial length of the appendix is between 8 and 75% of the total length of the lip and more particularly between 20 and 60% thereof.
• the ratio of the axial length of the appendage to the radial thickness of the distal axial abutment surface is less than 3.
• each sealing surface on the lip is a surface chosen from the group of conical, toric or complex surfaces comprising a combination of conical surfaces, cylindrical surfaces and / or one or more toric surfaces.
• one or at least one sealing surface on the lip is a complex surface comprising two portions of surfaces tangent to each other, namely a conical portion located on the side of the distal axial abutment surface and a toric portion of large radius, for example greater than 20 mm, located on the thread side, the corresponding sealing surface on the other threaded element being a conical surface of conicity substantially identical to that of the conical portion of the sealing surface on the lip and of axial width adapted to the total axial width of the sealing surface on the lip.
• Such a complex surface configuration allows, independently of the presence or not of an appendage, to increase the integrated contact pressure over the width of the sealing surface on the lip.
• each sealing surface on the lip has an average inclination of at least 10 ° relative to the axis of the threaded joint.
• the sealing surface on the lip has an axial width less than or equal to 10 mm and preferably less than or equal to 5 mm.
• the distal axial abutment surface is a flat surface perpendicular to the axis of the threaded joint or a conical surface coaxial with the threaded joint of half-angle at the apex between 70 ° and 90 °, which tends in this latter case to favor the contact between the sealing surface on the lip and the corresponding sealing surface.
• Figure 1 shows in axial half section a tubular threaded assembly sleeved from the prior art.
• FIG. 2 shows in axial half-section a tubular threaded assembly sleeved according to the invention.
• Figure 3 shows in axial half section an integral tubular threaded assembly for underwater riser according to the invention.
• Figure 4 shows in axial half section an integral tubular threaded assembly according to the invention called "flush", that is to say having no disturbance of outside or inside diameter at the tubular threaded joint.
• FIG. 5 represents an enlargement of the free end of the male threaded element of FIG. 2.
• Figure 6 shows the free end of Figure 5 after assembly with the corresponding female parts.
• FIG. 7 represents an enlargement of the free end of the male threaded element of FIG. 3.
• FIG. 8 schematically represents the free end of the male threaded element of FIG. 1 (state of the art).
• Figures 9 to 11 show schematically and compared to Figure 8 three variants of this free end according to the prior art.
• FIG. 12 represents a graph of the contact width and the integrated contact pressure over this width at the distal axial abutment surface and the sealing surface on the lip as a function of the axial tensile load exerted on the tubular threaded joint of Figure 1 (state of the art).
• FIG. 13 represents the same graph for the tubular threaded joint according to the invention of FIG. 2.
• FIG. 14 schematically represents a few male threads assembled with a few female threads on the tubular threaded joint of FIG. 2.
• Figures 15, 16 and 17 schematically show arrangements of the threaded elements during the engagement of these elements before screwing in the event of either radial ( Figures 15, 16) or angular ( Figure 17) misalignment.
• FIG. 1 represents a threaded sleeved assembly 200 of the state of the art between two tubes 101, 101 ′ which are tubular components of great length by means of a sleeve 202 which is a tubular component of short length.
• tube or tubular component of very long is meant tubes of several meters in length, for example about 10 m in length.
• Assemblies 200 are commonly used to form columns of casing or production tubes for hydrocarbon wells, risers underwater (risers) or drill string for these same wells.
• the tubes can be made of all kinds of non-alloyed, low-alloyed or highly-alloyed steels, or even ferrous or non-ferrous alloys heat-treated or cold-worked depending on the operating conditions such as for example: level of mechanical stress, corrosive nature of the fluid inside or outside the tubes.
• steel tubes which are not very resistant to corrosion and which have a coating, for example of synthetic material, preventing any contact between the steel and the corrosive fluid.
• the tubes 101, 101 ' are provided at their ends with identical male threaded elements 1, l' and are assembled by means of a sleeve 202 provided at each end with a female threaded element 2, 2 '.
• the male threaded elements 1, l ' are respectively assembled by screwing into the female threaded elements 2, 2' by constituting two symmetrical threaded joints 100, 100 'joined by a heel 10 a few centimeters in length.
• the heel 10 of the sleeve has an internal diameter substantially identical to that at the end of the tubes 101, 101 ′ so that the flow of the fluid circulating internally is not disturbed.
• tubular threaded joints 100, 100 ′ being symmetrical, the operation of only one of these joints will be described, for example the threaded tubular joint 100.
• the free end 7 constitutes an annular surface of axial abutment called surface axial stop distal disposed substantially transversely.
• Adjoining the free end 7 on the outer surface of the lip 11 is a conical surface 5 forming a male sealing surface on the lip; its taper is greater than that of the male thread 3.
• the female element 2 comprises means combined with those of the male element 1, that is to say that they correspond in form and are arranged to cooperate by their arrangement on the female threaded element with the male means of the male threaded element.
• the female element 2 thus internally comprises a conical female thread 4 and a non-threaded part between the thread and the heel 10.
• This non-threaded part comprises in particular an annular axial abutment surface 8 of substantially transverse orientation forming a shoulder at the end of the heel and a conical surface 6 forming a female sealing surface immediately adjacent to the shoulder on the side of the thread 4.
• the surfaces 5, 6 thus constitute metal-to-metal sealing surfaces which aim to seal the threaded seal even for high internal or external fluid pressures, gaseous fluids and for various stresses (axial traction, axial compression, bending , torsion %), simple or combined, static or fluctuating.
• Such threaded joints are said to be superior (or "premium”) in view of their performance compared to standard tubular threaded joints such as those defined by the API 5CT specification.
• Tubular threaded joints such as 100 in FIG. 1 must nevertheless face contradictory geometric requirements explained in diagrammatic figures 8 to 10.
• the length and thickness of the lip at the lip sealing surface must be sufficient to obtain a given radial stiffness of the lip which behaves like a spring (see FIG. 8); the contact pressure for a given radial interference thus varies with the radial stiffness of the lip 11.
• the lip flexes, which induces a deterioration of the angles of the sealing surfaces 5 and 6 and therefore a reduction in the effective contact width. and integrated contact pressure.
• the flexion of the lip due to the fluid pressure is all the more important as the lip part 35 between the start of the thread 3 and the sealing surface on lip 5 is long.
• the end of the lip can be conified before machining the bearing 5 so that its inner peripheral surface has a smaller diameter towards its end (FIG. 11); such conification however requires an additional manufacturing operation.
• Figure 2 shows a tubular threaded joint according to the invention directly derived from that of Figure 1 in particular by modification of the structure of the lip 11 which has an appendage 13, the structure of the female threaded element being adapted accordingly by moving back the female axial abutment surface towards the center of the sleeve 202; the axial length of the heel 10 of FIG. 2 is therefore shorter than in FIG. 1.
• FIG. 5 shows in detail the structure of the male lip 11 of the threaded joint of FIG. 2.
• the male lip 11 of total length l t has a sealing surface on lip 5 of total axial width l s which is separated from the distal axial stop surface 7 by an appendage 13 of axial length l a .
• the distal axial abutment surface 7 is a concave conical surface, coaxial with the threaded joint and with a half-angle at the top 75 ° (angle of 15 ° relative to the normal to the axis). Such an arrangement is known to increase the contact pressure between sealing surfaces 5, 6 on threaded joints of the type of FIG. 1.
• the appendix 13 has a cylindrical outer peripheral surface 19 which is connected to the distal axial abutment surface 7 by a toric surface of small radius R4.
• the axial length of the appendix l a represents in the case of FIG. 5 approximately 25% of the total axial length of the lip l t , these distances being taken relative to the point of intersection of the surfaces 7 and 19.
• the ratio between the axial length of appendix l a and the radial thickness ⁇ of the distal axial abutment surface is approximately 0.9. Too high a ratio greater than 3 may cause the appendix to buckle.
• the sealing surface on lip 5 is a complex surface markedly inclined on the axis (average inclination close to 15 °) and it is connected on the one hand to appendix 13 by a toric surface of small radius R3 and of on the other hand to the thread side lip by another toric surface of small radius R2.
• R3, R4 have for example a value of the order of 0.5 to 1 mm; R2 has a value of around 5 mm.
• the sealing surface on lip 5 consists of:
• the conical + toric geometrical configuration with a large radius on the thread side makes it possible to obtain a stable contact in width between sealing surfaces 5, 6 while the radial interference between sealing surfaces 5, 6 and / or between conical threads 3 , 4 and the application of internal fluid pressure tend to put the lip 11 "in banana" by slightly varying the inclination of the male sealing surface by a fraction of a degree. Such a variation in inclination tends on conical sealing surfaces to substantially reduce the effective contact width and the integrated contact pressure over the span width.
• a toric portion with a large radius RI on the thread side (RI preferably between 30 and 120 mm, in this case 60 mm) makes it possible to retain the advantages of a conical sealing surface under service conditions (stability operating range).
• Figure 6 shows the cooperation of the means arranged on the male lip 11 and on the corresponding female part in the assembly position.
• the female threaded element comprises a female axial abutment surface 8 which is conical convex, with a half-angle at the top equal to or substantially equal to that of the distal surface 7 and which forms a shoulder.
• the internal peripheral surface of the female threaded element between the female sealing surface 6 and the female axial abutment surface is arbitrary as long as it does not interfere radially with the external peripheral surface 19 opposite the appendix 13 .
• a short radius is provided to connect this female peripheral surface to the female axial stop surface 8.
• sealing surface 5 not at the free end of the lip limits the bending of the lip when the threaded joint is subjected to the internal or external pressure of a fluid and thereby limits the reduction in effective contact width and that of integrated contact pressure between sealing surfaces 5, 6 for threaded joints subjected to such internal or external pressures, in particular internal pressures.
• FIGS. 12 and 13 illustrate a certain advantage of the threaded joint according to the invention of the type of FIG. 2 (FIG. 13) compared to the similar threaded joint of the prior art of FIG. 1 (FIG. 12).
• the threaded joint of the prior art studied corresponds to a VAM TOP ® upper tubular threaded joint according to VAM ® catalog n ° 940 published by Vallourec Oil & Gas in July 1994 for tubes with external diameter 244.48 mm and thickness 13.84 mm (9 "5/8 x 53.5 lb / ft) in grade L80 (minimum yield strength 551 MPa).
• the variation of the effective contact width and the integrated contact pressure over this width has been studied by numerical calculation according to the finite element method (FEA) for the abutment surfaces 7, 8 and for the sealing surfaces 5, 6 on a threaded joint screwed to the nominal screwing torque as a function of the axial tensile load to which the threaded joint is subjected, expressed in% of the load corresponding to the elastic limit of the body of the tubes (PBYS).
• FEA finite element method
• Curve C relating to the evolution of the contact width between sealing surfaces indicates an effective contact width decreasing from 1.5 to 1.1 mm when the axial tensile load goes from 0 to 100%.
• sealing surfaces according to the tested geometry correspond however to those 5 and 6 of Figures 5 and 6 (male conical bearing at 50% taper + toric of 60 mm radius) which are considered to improve the stability of the contact under load compared to simple tapered bearings.
• Curves A, B and C in Figure 13 are quite similar to those in Figure 12.
• the main difference relates to the evolution of the integrated contact pressure between sealing surfaces (curve D) which decreases much less quickly on the threaded joint according to the invention so that the threshold of 437 N / mm (straight line S) n 'is crossed only above a load corresponding to 89% PBYS.
• the criterion on integrated contact pressure which is a severe criterion, recently introduced by users very concerned about the sealing guarantees on threaded joints, is met for a wide range of service conditions on the threaded joint according to invention.
• the low axial stiffness of the lip 11 resulting from the presence of the appendage 13 contributes to the better sealing performance under tension of the threaded joints according to the invention. This low axial stiffness first of all induces a favorable increase in the radial stiffness for the sealing performance of the threaded joint.
• the low axial stiffness also allows the lip to store at the end of screwing a large deformation in axial compression, deformation which can then advantageously be restored when the threaded joint is subjected to axial tensile loads.
• An appendage that is too long (l a > 75% l t ) may cause buckling of the lip and a reduction in sealing performance.
• the lip and the means associated therewith (5, 7, 13) are moreover relatively easy to produce by machining.
• a first additional advantage concerns the precision on the real tightening torque.
• the threaded joints are generally screwed into position using mechanical or hydraulic machines called “screwing wrenches” which develop significant torques since the threaded joint must be screwed beyond the docking of the axial abutment surfaces.
• the actual torque obtained can be offset from the desired nominal torque. This offset depends on many factors and can be reduced by reducing the tightening speed, which affects the productivity of the tightening.
• the reduction in axial stiffness of the lip on the threaded joint according to the invention makes it possible to obtain a less steep torque rise curve between docking and final assembly position and therefore either to obtain less difference between nominal torque and real tightening torque is to allow faster screwing.
• Another additional advantage concerns the behavior of the tubular threaded joint under axial compression load.
• FIG. 14 illustrates the appearance of male 21 and female 22 trapezoidal threads of a threaded joint with conical threads screwed in position.
• the male threads 21 have a top of the thread 29, a bottom of the thread 27 both inclined at an angle C (for example 1.8 °) on the axis, a carrying flank 23 and an engagement flank 25.
• the female threads 22 likewise have a top of the thread 28, a bottom of the thread 30, a carrying flank 24 and an engaging flank 26.
• the female thread tops 28 interfere radially with the male thread bottoms 27 while there is a set of male thread tops 29 and female thread bottoms 30 .
• a low axial lip stiffness makes it possible to bring the engagement flanks into contact
• the threaded joint according to the invention therefore also has excellent mechanical resistance characteristics in axial compression.
• FIG. 3 represents another type of tubular threaded joint according to the invention, for underwater risers known as "work over risers”.
• the threaded joint 300 is of the integral type, the male threaded element 1 being produced at the end of a first tube 101 and the female threaded element 2 at the end of a second tube 102 by machining the tubes.
• the threaded elements 1 and 2 may result from a fattening of the tube ends by forging (increase in the outside diameter and / or decrease in the inside diameter).
• the male and female threaded elements can be attached to the tubes, for example by welding.
• This type of threaded joint has 2 pairs of axial abutment surfaces, each pair comprising a distal axial abutment surface.
• a first pair called “internal stop” is constituted as above by a distal surface 7 at the free end of the male threaded element 1 and an annular surface 8 forming a shoulder on the female threaded element 2.
• the other pair called “external stop” is made up symmetrically of a distal surface 18 at the free end of the female threaded element 2 and an annular surface 17 forming a shoulder on the male threaded element 1.
• All 4 axial abutment surfaces are flat, perpendicular to the axis of the threaded joint 300.
• a lip 11, 12 separates each stop from the threads.
• the female lip 12 does not have a sealing surface.
• the male lip 11 (see FIG. 7) has a sealing surface on the lip 5 axially separated from the distal axial abutment surface 7 by an appendage 13.
• the sealing surface 5 is a complex surface formed on the free end side by a conical portion 33 inclined at 50% and on the threading side 3 by a toric portion 31 of radius RI (40 mm) tangent to the conical portion 33, the scope female sealing element 6 being simply conical with a 50% conicity and an axial width adapted to that of the total male sealing surface 5.
• Appendix 13 has an outer peripheral surface 19 of cylindrical shape and has an axial length l a of 5 mm representing approximately 9% of the total axial length of lip l t .
• the ratio of axial appendage length to radial thickness of the distal axial abutment surface is approximately 0.75.
• the lip part located between sealing surface on lip 5 and thread 3 comprises on its outer peripheral surface 35 two cylindrical surfaces 37 and 39, the surface 39 starting at the foot of the thread 3 being of smaller diameter D2 than the surface 37 of the sealing surface side (diameter Dl) with (D2 - Dl) being worth approximately
• Such a step increases the radial stiffness of the sealing surface on lip 5 and therefore the contact pressures between sealing surfaces 5, 6. It also reduces the "banana" deformation of the lip when the threaded joint 300 is subjected at the pressure of an external fluid. It also contributes, in combination with appendix 13, to protecting the sealing surface 5 from damage marks in the event of misalignment when the threaded elements are engaged.
• Table 1 gives integrated contact pressure values over the contact width at the sealing surfaces obtained by numerical calculation at the end of tightening and under axial traction.
• table 1 Integrated contact pressure between sealing surfaces.
• the integrated contact pressures are higher and decrease a little less quickly on the threaded joint according to the invention for this configuration with first docking of the external abutment surfaces.
• the appendix having a very limited length (9% of the total length of lip) and the lip 11 being very stiff radially (10 mm thick at the level of the step 37), the differences compared to the threaded joint of the state art are less than in the previously described example (VAM TOP ®).
• FIGS. 15, 16, 17 show on the threaded joint 300 of FIG. 3 the limit conditions of engagement of the threaded elements taking into account the presence of appendix 13.
• FIG. 15 shows the maximum possible radial misalignment d3 at the very start of the engagement of the threaded elements 1 and 2, the male sealing surface on lip 5 coming into contact with the female free end 18: d3 can exceed 10 mm for the threaded joint 300 of the dimensions indicated above.
• FIG. 16 shows the maximum possible radial misalignment d4 a little later when the male sealing surface on lip 5 comes into contact with the 1st female thread: d4 is worth approximately 8 mm for the threaded joint considered.
• FIG. 17 shows the maximum possible angular misalignment E, the male sealing surface on lip 5 being in contact with the female thread and the male and female threads not yet engaged: E is approximately 4 °.
• Appendix 13 of course protects the sealing surface on lip 5 from axial impact at the end during handling on site. Note that in the case of FIG. 17, the appendix also makes it possible to create a protection or radial barrier for the conical portion 33 of the sealing surface on the lip, which is the most critical portion for sealing.
• the entire sealing surface can also be protected if, as shown in FIG. 5, the appendix 13 has an axial length l a such that the sealing surface on lip 5 is located on the side of the element. threaded with respect to the straight line Dl which passes through the top of the 1st male thread and which tangents the free end of the threaded element.
• the straight line D1 materializes for example the generator of the vertices of female nets in FIG. 17.
• FIG. 4 represents an integral threaded joint 400 called "flush" with constant internal and external diameter, with internal (7, 8) and external (17, 18) abutment surfaces and with 2 pairs of sealing surfaces: an internal pair (5, 6) and an external pair (15, 16).
• the threaded joint 400 is waterproof both to external pressures thanks to the external pair of sealing surfaces and to internal pressures thanks to the internal pair of sealing surfaces.
• the male sealing surface 5 of the internal pair and the female sealing surface 16 of the external pair are sealing surfaces on the lip.
• the mechanical resistance to compression is also improved.
• the low axial stiffness of the lips 11, 12 makes it possible to continue the screwing sufficiently after the landing of a pair of internal or external abutment, preferably internal, until axial abutment of the second pair of abutment surfaces.
• the present invention is not capable of being limited to the tubular threaded joints which have just been described.
• tubular threaded joint in particular for example having conical or cylindrical threads, with one or more threaded parts, stepped or not, with trapezoidal or triangular threads, with so-called “corner” threads whether wide or not variable.

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