WO2002065012A9 - Joint filete tubulaire a filets trapezoidaux avec face de filet bombee convexe - Google Patents
Joint filete tubulaire a filets trapezoidaux avec face de filet bombee convexeInfo
- Publication number
- WO2002065012A9 WO2002065012A9 PCT/FR2002/000420 FR0200420W WO02065012A9 WO 2002065012 A9 WO2002065012 A9 WO 2002065012A9 FR 0200420 W FR0200420 W FR 0200420W WO 02065012 A9 WO02065012 A9 WO 02065012A9
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- convex
- flank
- thread
- threads
- male
- Prior art date
Links
Classifications
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- 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
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- E—FIXED CONSTRUCTIONS
- E21—EARTH DRILLING; MINING
- E21B—EARTH DRILLING, e.g. DEEP 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
- F16L15/001—Screw-threaded joints; Forms of screw-threads for such joints with conical threads
- F16L15/002—Screw-threaded joints; Forms of screw-threads for such joints with conical threads with more then one threaded section
-
- 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 comprising a male threaded element and a female threaded element with trapezoidal threads arranged at the end of tubes to be assembled, the threaded elements being able to be arranged as a pin at the end of very long tubes as of short tubes. such as sleeves.
- Such tubular threaded joints are used in particular to form columns of casing or production tubes or drill pipe sets for hydrocarbon wells or for similar wells such as wells for geothermal energy.
- the trapezoidal threads include a flank of engagement of the thread side directed towards the free end of the threaded element considered, a flank worn on the affixed side of the threads, a thread top of non-zero width and a bottom of net also of non-zero width, the supporting flanks and the engaging flanks being oriented substantially perpendicular to the axis of the element -thinned (inclination of +3 "for the supporting flanks, of +10 ⁇ for the flanks for example in the case of the APl Buttress net).
- Trapezoidal threads are thus defined in this document as opposed to other types of threads defined by the abovementioned API specifications, namely triangular or rounded triangular (“round”) threads whose bearing and engagement flanks are strongly inclined compared to normal to the axis of the threaded element (30 ° for example) and whose vertices and bottom of the thread are of substantially zero width, they have significant advantages over triangular or round threads. -vis the unacceptable risk of fjump ouf ngrè ⁇ ement ").
- tubular threaded joints with trapezoidal threads according to A have been the subject of numerous developments, in particular to improve the resistance to very diverse stresses resulting from the operating conditions (axial traction, axial compression, bending, twisting, internal or external pressure ...) and their tightness to the fluids circulating inside or outside of these joints under such stresses. These improvements are for example described in the documents EP 488 912, EP 707 133, EP 454 147, WO 00/14441.
- the faces of the trapezoidal threads of the threaded joints of the state of the art that is to say the flanks of the threads as well as the tops and bottoms of threads appear rectilinear in axial section except at the level of the connections between faces, connections which generally have a connection radius or a chamfer; this is why we will call such faces in this document rectilinear faces.
- contact with contact pressure is developed between at least one face of the male thread and the corresponding face of the female thread.
- this contact pressure can develop between peaks and combined thread bottoms, between load flanks, between engagement flanks or between several of these faces.
- An oversteer can notably occur during the descent in rotation of a column of tubes at the bottom of deviated or even horizontal oil wells and cause a relative positioning deviation of the male and female elements with the harmful consequence a risk of leakage of the threaded joints.
- the tubular threaded joint comprises a male threaded element at the end of a first tube and a female threaded element at the end of a second tube.
- the male threaded element externally comprises a male thread with trapezoidal threads over substantially the entire length of the thread and the female threaded element internally comprises a female thread conjugate with the male thread, that is to say in shape and layout adapted to their screwing.
- the male and female threaded elements are screwed into each other under a given screwing torque so that at least one face of male thread is under contact pressure with the corresponding face of the female thread.
- thread means a thread in one or more threaded parts.
- the threads are trapezoidal over substantially the entire length of each of the threaded parts.
- At least one face of the thread under contact pressure of a thread has, before screwing, a convex convex shape continuous over the width of the face considered and is in so-called point contact with the corresponding face of the conjugate thread.
- convex convex face is understood to mean a thread face which appears as convex curvilinear in axial section.
- concave curved face and rectilinear face respectively means faces which appear as such in axial section (except at the level of the connections with the adjacent faces).
- face width designates in this document the dimension of the face seen in axial section.
- face width therefore designates the essentially axial dimension of vertices or bottom of the net and the essentially radial dimension of the flanks.
- trapezoidal thread corresponds to the general definition which has been given above even if certain faces are not rectilinear in the case of the present invention. It covers trapezoidal nets with angles of load flanks and engagement as positive as negative or zero (square, hook, semi-dovetail or dovetail nets), the sign convention being illustrated in the embodiments described later in the text.
- a convex convex face as defined creates with the corresponding face of the conjugate thread a contact which appears, in a section passing through the axis of the assembly, as punctual or substantially punctual provided, of course, that the radii of curvature of the faces are adapted.
- the contact pressure resulting from said point contact is maximum at the point of contact and decreases on each side of this point more or less rapidly depending on the differences in radius of curvature of the two faces in contact and the elasticity characteristics of the materials in contact. .
- the curvature of the convex convex face is chosen so that the threaded joint according to the invention has, once screwed under the given screwing torque compared to a conventional threaded joint in which all the faces of male and female threads are rectilinear, a resistance substantially increased when unscrewing or overfitting
- the curvature of said convex curved face is also adapted to the geometry of the corresponding face in contact so that the maximum pressure does not lead to a plasticization of the material of the faces in point contact.
- said convex curved face has over its width except at the connections with the adjacent faces one or more radii of curvature between 2 and 60 mm and preferably between 3 and 20mm.
- Said convex curved face can be produced over all or part of the length of the thread considered but it is preferably carried out over the entire length of the thread considered and therefore over the entire length of each of the threaded parts when the thread comprises several threaded parts.
- said convex curved face has a uniform curvature over the width of the face considered except at the level of the connections with the adjacent faces.
- said convex curved face has a uniform curvature over the entire length of the thread.
- a convex convex face corresponds with a straight face on the conjugate thread.
- the male and female threads of the threaded joint are conical with threads interfering radially with one another and said convex convex face is a top of thread.
- said convex convex face is a male or female flank of the thread and one or other of the threads, male or female, comprises means for making the convex curved flank or flexible the side corresponding to this on the conjugate thread.
- the convex curved flank is a load-bearing flank.
- the convex curved flank is an engagement flank.
- said bending of the side thus qualified as flexible in the remainder of this document increases with the contact pressure during or at the end of screwing and in particular allows the threads to adapt to the dimensional dimension deviations of the male and female threads with respect to the dimensions. nominal without generating excessive contact pressure.
- said means for making the convex convex flank or the flank corresponding to it flexible is a groove disposed on the top of the thread adjacent to the flexible flank.
- the depth of the groove is less than or equal to the height of the net where it is made.
- the groove has at its outlet a width less than or equal to 2/3 of the width of the net where it is made, the width of the net being measured at mid-height thereof.
- the bottom of the groove is rounded along a radius greater than or equal to 0.2 mm.
- the angle called “convex curved flank angle” formed by the tangent to the convex curved flank at mid-height thereof and the normal to the axis of the assembly is different from the angle called “corresponding flank angle” formed by the tangent to the flank corresponding to the convex convex flank also taken halfway up said corresponding flank and the normal to the axis of assembly.
- the values of the convex curved flank angle and the corresponding flank angle are such that the first contact between the flank convex convex and the corresponding side takes place on the flexible side on the side of the top of the net where the groove is located.
- the sign of the algebraic value of the offset between the convex curved flank angle and the corresponding flank angle is such that the point of contact between the convex curved flank and the corresponding flank moves during screwing towards the center of rotation of the flexible side.
- the value of the offset between the convex curved flank angle and the corresponding flank angle is such that the final point of contact between the convex curved flank and the corresponding flank once the threaded joint is completely screwed is located in outside the quarter width of the convex curved side located at the end of the latter on the net end side.
- the absolute value of the offset between the convex curved flank angle and the corresponding flank angle is between 1 and 5 e .
- each male and female element comprises at least one sealing surface, each male sealing surface radially interfering with a corresponding female sealing surface on the tubular threaded joint in the screwed state in position.
- each male and female element comprises at least one annular transverse abutment surface, at least one male abutment surface being in abutment against a corresponding female abutment surface on the tubular threaded joint at l screwed in position.
- Figure 1 depicts a threaded sleeve connection comprising two threaded joints with conical threads and trapezoidal threads.
- FIG. 2 describes an integral threaded assembly comprising a threaded joint with two-stage cylindrical threads and trapezoidal threads.
- FIG. 3 describes some trapezoidal threads of a threaded joint according to the invention of the type of FIG. 1 in which the female thread tops are convex convex: FIG. 3A relates to the female thread alone, FIG. 3B relates to the thread male only and FIG. 3C relates to the completed assembly of the elements of FIGS. 3A and 3B.
- FIG. 4 describes some threads of another threaded joint according to the invention, the threaded joint being of the type of FIG. 1 with trapezoidal threads with axial shrinking, the male engagement flank of which is convexly convex.
- FIG. 5 describes a variant of the threaded joint of FIG. 4.
- FIG. 6 describes some threads of another threaded joint according to the invention, of the type of FIG. 2 with trapezoidal threads with variable width corners, the male carrying flank of which is convexly convex.
- Figures 4 to 6 each include 4 sub-figures identified by the indices A to D:
- the index A relates to the female thread alone while the index B relates to the male thread only.
- the index C relates to the assembly of the elements of the indices A and B during screwing at the point where the corresponding faces come into contact.
- Index D refers to the completed assembly of elements of indices A and B.
- FIGS 1 to 6 are not to scale, the characteristics of the threaded joints having been exaggerated to better highlight them or better understand their operation.
- FIG. 7 represents the distribution of the contact pressures between the male top and female bottom of interfering trapezoidal threads, FIG. 7A being related to the contact between rectilinear top and bottom of a threaded joint of the prior art and FIG. 7B in contact between rectilinear bottom and convex convex top of the threaded joint of FIG. 3C.
- FIG. 8 is a graph representing the displacement of the fretting contact point in the case of the threads of FIG. 4 as a function of the screwing for different angular configurations of the engagement flanks.
- FIG. 9 is a graph showing the rotation of the flexible engagement flank of FIG. 4 as a function of the screwing for different angular configurations of the engagement flanks.
- FIG. 10 is a graph showing the displacement of the fretting contact point in the case of the threads of FIG. 4 as a function of the screwing for different radii of curvature of the convex convex face.
- Figure 11 shows some threads of another threaded joint according to the invention of the type of Figure 1 with conical threads with interfering trapezoidal threads.
- FIG. 1 represents a threaded sleeve assembly 200 between two very long tubes 101, 101 ′.
- tube of great length is meant tubes of several meters in length, for example about 10 m in length.
- Such tubes are commonly assembled to form columns of casing or production tubes for oil wells or drill string for the 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 to adapt to different service conditions: level of mechanical stress, corrosive nature of the fluid inside or outside the tubes. It is also possible to use 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, 1' 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, 1 ' are respectively assembled by screwing in 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 of the tubes 101, 101 ′ so that the flow of the fluid circulating internally is not disturbed.
- the threaded joints 100, 100 ′ being symmetrical, the operation of only one of these joints will be described.
- the male threaded element 1 comprises a male thread 3 with trapezoidal threads derived from the type known as "Buttress" according to API specification 5B; this male thread 3 is conical and disposed on the outside of the male element and it is separated from the free end 7 of said element by a non-threaded lip 11.
- the free end 7 is a substantially transverse annular abutment surface.
- Adjoining the free end 7 on the outer surface of the lip 11 is a conical surface with a bearing surface 5 whose conicity 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 shape and are intended to cooperate by their arrangement with the male means.
- 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 surface of substantially transverse orientation of stop 8 forming a shoulder at the end of the heel and a conical surface of bearing 6 following the shoulder.
- the bearing surfaces 5, 6 thus constitute sealing surfaces which make the threaded seal watertight even for high internal or external fluid pressures and for various stresses (axial traction, axial compression, bending, torsion, etc.).
- sealing ring made of synthetic material such as a fluoropolymer in order to produce or reinforce the sealing.
- FIG. 2 Another example of a threaded connection between two very long tubes is illustrated in FIG. 2, this type of connection 300 which implements only one threaded joint being qualified as integral.
- the tube 301 is provided at one of its ends with a male threaded element 1, the second tube 302 being provided with a female threaded element 2 at the corresponding end.
- the male threaded element 1 comprises an external male thread constituted in the case of FIG. 2 of two stages or cylindrical steps 303, 303 ′, with trapezoidal threads separated by a transverse annular surface 307 of a central shoulder forming a stop, the step of smaller diameter 303 'being disposed on the free end side 309' of the element, which free end 309 'is a transverse annular surface.
- the threaded part 303 is extended by a non-threaded part comprising a conical bearing surface 311 and a transverse annular surface 309 forming a shoulder.
- the female threaded element 2 internally comprises female means combined with male means.
- the female element 2 thus comprises a female thread consisting of 2 cylindrical steps 304, 304 ′ separated by a transverse annular surface 308 of a central shoulder forming a stop, the step of larger diameter 304 being disposed towards the transverse annular free end 310 of the female element.
- the female element further comprises two conical surfaces of bearing 312, 312 'corresponding to the male bearing surfaces 311, 311' and a transverse annular surface 310 'forming a shoulder at the end of the element opposite the free end 310 .
- the male threaded parts 303, 303 ' are screwed respectively into the female threaded parts 304, 304' and the abutment surfaces of the central shoulders 307, 308 are in abutment against one another.
- the transverse end surfaces 309, 309 ′ are in quasi-contact with those of shoulder respectively 310, 310 ′ and constitute auxiliary stops for the central main stop 307, 308.
- the sleeve threaded assembly can be with cylindrical threads and the integral assembly with conical threads.
- the threads can also each have two conical threaded parts of identical or different taper or of the cylindro-conical type, the threaded parts of the same thread being able to be stepped or not stepped.
- FIGS. 1 and 2 the threads have been shown diagrammatically by the generators or the covers of the top of the thread and of the bottom of the thread.
- the following figures describe the threaded joint threads according to several variants of the invention.
- FIG. 3 relates to conical threads with radially interfering trapezoidal threads and to convex convex thread summits of a threaded joint 100 of FIG. 1.
- FIG. 3B represents the male threads 21 of this type of threaded joint which have a conventional trapezoidal shape in axial section and which comprise a carrying flank 23, an engaging flank 25, a thread top 29 and a thread bottom 27.
- Their height is h1 and their width at half height is 2.5 mm (thread of the type 5 threads per inch).
- the vertices and bottom of the threads are arranged on conical surfaces of the same conicity defined by the half-angle at the vertex ⁇ between the "primitive" cone symbolized by its generatrix 37 and the direction of the axis of the assembly.
- the thread tops 29 and the thread bottoms 27 are rectilinear except at the level of the connections with the sides; these connections have, in a manner known per se, a radius of the order of a fraction of mm to limit the stress concentrations of the thread bottoms and the brittleness of the edges; the thread tops 29 and the thread bottoms 27 are arranged on conical surfaces with a half-angle at the top ⁇ .
- the supporting flanks 23 and engagement 25 are also rectilinear and form an angle ⁇ and ⁇ respectively with the normal to the axis of the assembly.
- ⁇ is slightly negative (the flank 23 somewhat overhangs the bottom of the thread 27) while the angle ⁇ is positive and more inclined.
- the female threads 22 are shown in FIG. 3A. Their shape is substantially trapezoidal and suitable for screwing with the male threads 21. Their height h2 is slightly greater than that h1 of the male threads 21 and their width at half height is 2.5 mm (thread of the type 5 threads per inch) .
- the female thread tops 128 and female thread bottoms 30 are tangent to or are arranged on conical surfaces with a half-angle at the top ⁇ identical to that relating to the female threads.
- the female thread bottoms 30 are rectilinear except at the connections with the sides which, like the male threads, have a connection radius.
- the female thread tops 128 are convexly convex over their entire width, that is to say that they have no discontinuity over their width.
- the supporting flanks 24 and engagement 26 respectively make the same angles ⁇ and ⁇ with the normal to the axis of the assembly as the corresponding flanks 23, 25 of the male thread.
- the curvature of the convex convex female thread top 128 makes it possible to increase the resistance to unscrewing or overfitting the threaded joint according to the invention.
- FIG. 7A schematically shows the distribution of the contact pressures on a threaded joint of the state of the art between a female thread top 28 of rectilinear shape and a corresponding male thread bottom 27 also of straight shape.
- the arrows P c give the measurement of the local contact pressure at each point of the distributed contact; it is noted that the values of contact pressure P c are higher at each end R, S, T, U of the contact segments.
- FIG. 7B shows that a small curvature of the female thread tops 128 makes it possible to eliminate the median contact pressure trough and therefore the trapping of the lubricant between the female thread tops 128 and the interfering male thread bottoms 27, on the contrary creating a median contact pressure peak.
- a radius of curvature R3 that is too small leads to a median peak in contact pressure that is too pronounced and consequently to a risk of plasticization of the material and / or seizure of the threads after several uses of the threaded joints; it also induces a reduction in the width of the supporting flanks 23, 24 and therefore in the maximum acceptable axial traction load: a radius of curvature R3 greater than or equal to 2 mm is entirely suitable.
- a radius of curvature R3 less than or equal to 60 mm and preferably 20 mm is adequate .
- FIG. 4 relates to conical threads with trapezoidal threads with axial hooping of a threaded joint 100 of FIG. 1.
- trapezoidal threads with axial hooping means threads as described in document WO 00/14441 in which the width of the threads at half height is greater than the width also at half height of the spaces between corresponding threads of the conjugate thread, this which induces axial hooping of the two flanks of a thread by those of the conjugate thread and vice versa.
- FIG. 4B represents a few male threads 21 which have a substantially trapezoidal shape in axial section and which comprise a carrying flank 23, an engaging flank 125, a thread top 29 and a thread bottom 27.
- the vertices and bottom of the threads are rectilinear (except at the level of the connections with the flanks which have a radius of the order of a fraction of mm to limit the stress concentrations of the bottom of the thread and the brittleness of the edges) and are arranged on conical surfaces of the same conicity defined by the half-angle at the top ⁇ between the "primitive" cone symbolized by its generatrix 37 and the direction of the axis of the assembly.
- the threads have, throughout their entire length, a helical groove 31, the profile of which has an axis substantially normal to that of the assembly which opens onto the top of the thread approximately at mid-width.
- the groove 31 has a V-shaped profile with a rounded bottom, the angle between the branches of the V is of the order of 35 ° and the radius at the bottom of the groove 61 is 0.4 mm.
- Its opening width is around 35% of the width of the top of the net 29 and its depth is around 60% of the height of the net 21.
- the supporting flank 23 is rectilinear (except at the level of the connections with the tops and the bottoms of the net as indicated above) and overhangs very slightly the bottom of the thread, the angle ⁇ of this load-bearing flank relative to the normal to the axis of the assembly being therefore very slightly negative, equal to -3 °.
- the engagement flank 125 which is adjacent to the top of the thread 29 is convexly convex over its entire width MP; it has a uniform radius of curvature R1 of several mm except at the level of the connections with the tops and bottom of the net where the radius of curvature is smaller, of the order of the fraction of mm.
- the tangent 39 to the engagement flank taken halfway up the net forms an angle A with the normal to the axis of the assembly.
- the width of the net taken halfway through the net is £ 1 while £ Z represents the space between the teeth of the net at mid-height, the sum (il + £ 3) being equal to the pitch of the net.
- FIG. 4A represents some female trapezoidal threads 22 of shape adapted to that of the male threads 21.
- the female threads 22 have 4 rectilinear faces (except at the level of the connections with the tops and bottoms of the net which have, in a manner known per se, a radius of the order of the fraction of mm to limit the stress concentrations of the bottoms of the net and the brittleness of the edges), namely:
- a supporting flank 24 which overhangs the bottom of the thread 30 and is inclined at an angle ⁇ with respect to the normal to the axis of the assembly, this angle ⁇ being identical to the angle of the male carrying flank, a flank d engagement 26 which is inclined at an angle B relative to the normal to the axis of the assembly, the angle B being slightly greater than the angle A in FIG. 4B, - a top of the thread 28 disposed on a conical surface with a half-angle at the top ⁇ identical to that of the conical surface relating to the male thread, a bottom of the thread 30 also disposed on a conical surface with a half-angle at the top ⁇ .
- the angles ⁇ and B are different, their difference ⁇ being such that the threads 22 are narrower at their apex 28 than at their base.
- £ 2 represents the width of the female net at half height while £ A represents the space between teeth of the female net at half height; the sum (£ 2 + £ A) represents the pitch of the female net which is identical to the pitch of the male net.
- FIG. 4C represents the position of male 21 and female 22 threads at the time of the first contact during screwing.
- the supporting flanks 23, 24 rectilinear with angle ⁇ are in contact distributed over their entire common width.
- the vertices of the threads 29, 28 are still distant from the corresponding thread bottoms 30, 27.
- the engagement flanks 125, 26 are in contact at the point O which is located on the arc MP closer to M than to P on the male flank 125 and also closer to Q than to N on the female flank 26. The contact therefore takes place on the side of the male thread top where the groove 31 is located.
- the groove 31 which opens onto the top of the thread 29 adjacent to the convex convex flank 125 allows the two parts 33, 35 of male thread 21 to be deformed by bending under the fretting contact pressure resulting from the continued screwing in. beyond the first contact: the groove 31 therefore makes it possible to soften the structure of the male thread 21 and to reduce the rigidity of the engagement flank 125.
- the deformation of the two parts 33, 35 of male thread is proportional to the contact pressure since the material of the male thread 21 is made to work in the elastic range, the solid female thread 22 being able to be considered in first approximation as rigid and the stiffness of the spring constituted by the thread part 35 between the groove 31 and the flexible engagement flank being determined by the geometry of this thread part 35 and by the elasticity of the material, for example the steel, of which it is made.
- the curvature of the convex convex male engagement flank 125 makes it possible to work the groove optimally: in the absence of such a curvature, that is to say if the male engagement flank was rectilinear at an angle equal to B, there would be approximation by translation of the parts 33, 35 of the male thread tooth, which would lead to a significant reduction in the radius R2 at the bottom of the groove and to a risk of shearing of the root of the thread parts 33 , 35.
- the curvature of the male engagement flank 125 allows, on the contrary, the progressive rotation of the convex convex engagement flank 125 thus made flexible during the continuation of the screwing, as well as a distribution of the contact pressures according to Hertz theory.
- the center of rotation of the flexible engagement flank 125 is substantially located at P, at the foot of the flexible engagement flank 125.
- Figure 4D illustrates the positioning of the threads at the end of screwing.
- the part 35 of the thread between groove 31 and flexible engagement flank 125 has rotated by a certain angle to allow adaptation of the space between flanks of male and female threads.
- the initial contact point O has moved in O 'towards the point P along the arc MP.
- Such displacement OO ′ is beneficial because it makes it possible not to always work the same point of the engagement flanks during screwing and therefore to limit the risks of seizing.
- the graph in FIG. 8 shows the displacement DC of the contact point O along the arc MP of the flexible flank 125 of FIG. 4 as a function of the tightening FA on the engagement flank for various values of the angle A included between 9 and 14.
- angle A less than 9 ° because the point O would then risk being outside the arc MP beyond M. Values of angle A greater than 12 ° are also not desirable since the final contact point O 'could be beyond P for certain pairs of male-female threaded elements that are poorly matched.
- FIG. 9 shows on the same threaded joints the evolution of the angle of rotation RFE of the flexible side 125 as a function of the tightening FA.
- the graph in FIG. 10 shows for the same type of threaded joint the influence for different radii of curvature R1 of the sidewall 125 the influence of the tightening FA on the displacement DC of the contact point, the angle A being kept constant and equal at 10 °.
- the initial contact takes place at M and the contact point quickly moves along the arc MP as and when tightening.
- the male threaded element is conventional with a male thread with rectilinear faces while the female threaded element comprises a female thread having a convex convex flank of engagement and a groove opening at the top of the female thread.
- FIG. 5 is a variant of FIG. 4.
- the male thread 21 also has a convex flank 125 convexly convex of angle A with half flank width, but it does not have a groove.
- a groove 32 is on the other hand disposed on the female thread 22 and allows the bending of the rectilinear female engagement flank 26 which corresponds to the convex convex engagement flank 125 in the condition of shrinking contact during screwing.
- the angle A is greater than the angle B.
- Such a configuration allows, as seen in FIGS. 5C and 5D, a first contact in O on the half-width of the engagement flank flexible 26 on the side of the female thread top 28 where the groove 32 is located. This configuration also allows the displacement OO ′ of the contact point towards the center of rotation Q.
- FIG. 6 shows the application to the threaded joint 300 of FIG. 2 of a thread with a convex groove and flank of engagement convex to a cylindrical thread with trapezoidal threads called corners or with variable width, such threads with corner threads being in particular known from US patent Re 30647.
- the male thread 303 ′ of FIG. 6B comprises threads of the trapezoidal type in dovetail and with variable width.
- the male trapezoidal threads 321 comprise: a straight top of thread 329 parallel to the axis of the threaded joint; - A thread bottom 327 also straight and parallel to the axis of the threaded joint; a straight flank 325 which overhangs the bottom of the thread 327, the angle ⁇ between flank and normal to the axis of the assembly being counted thereby negatively; a convex convex flank 323 of radius R1 (apart from the connections with the tops and the bottoms of the thread).
- the flank 323 is such that the tangent 339 at mid-height of the net forms an angle A with the normal to the axis of the assembly.
- angles ⁇ and A are such that the threads are wider at their top 329 than at their base (dovetail threads).
- These threads are said to be of constant pitch and of variable width because the thread width increases (and therefore the space between thread teeth decreases) when one moves away from the free end of the threaded element: there is thus £ 3.1 greater than £ 3.2 in FIG. 7B.
- the female threads 322 are of the type known as a dovetail with variable width and suitable for the male threads 321.
- the thread vertices 328 and thread bottoms 330 are straight and parallel to the axis of the assembly.
- the load-bearing 324 and engagement 326 sides are also rectilinear; they both overhang the thread bottoms 330 so that their respective angles B and ⁇ with respect to the normal to the axis of the assembly are counted negatively.
- the female threads 322 further comprise over their entire length a helical groove 332 whose profile has an axis substantially normal to the axis of the assembly and which opens onto the top of the thread 328.
- This groove has a V-shaped profile with rounded bottom of radius R2 equal to 0.4 mm.
- the point O is located on the segment NQ on the side of the top of the thread 328 where the groove 332 is located. This comes, as before, from the fact that the angle A is less than the angle B in absolute value.
- the function of the groove 332 advantageously aided by the convex convex shape of the supporting flank 323 is to allow such elastic deformation of the flanks.
- the functions of the groove 332 and of the convex curved flank 323 are similar to those of the grooves 31, 32 and of the convex curved flank 125 of FIGS. 4 and 5, the flexible flank 324 being rectilinear as in the case of FIG. 5.
- FIGS. 4 to 6 can also be adapted to conical threads with corner threads of variable width of the type disclosed in document WO 94/29627. Such an adaptation is easy for a person skilled in the art taking into account the preceding indications.
- tubular threaded joint with axial shrinking according to FIG. 4 which presents a radial interference between the tops of one of the threads, male or female and the bottom of the conjugate thread at the end of screwing.
- the height h1 of the male threads is slightly less than that h2 of the female threads and the width of the male or female threads is slightly less than that of the spaces between corresponding threads as in FIGS. 3A, 3B so that after screwing (fig. 11C) the female thread tops 28 interfere radially with the male thread bottoms 27 while there is a radial clearance between male thread tips 29 and female thread bottoms 30.
- the male 123 and female 24 supporting flanks are in support while there is an axial clearance between male 25 and female 26 engagement flanks.
- the female threads 22 are full while the male threads 21 have a groove 31 similar to that of FIG. 4, which makes it possible to accommodate the variations in contact pressure in service.
- the curvature of the male supporting flank 123 allows, in addition to the effects on the resistance to over-rolling and unscrewing, very advantageously, to control the width of the contact and the location of the contact between the supporting flanks 123, 24 as indicated above when the convex convex face is an engagement flank (see Figures 4 and 5). Similar effects could be obtained by producing a convex convex female carrying flank, the male carrying flank being rectilinear.
Abstract
Description
Claims
Priority Applications (9)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
MXPA03006962A MXPA03006962A (es) | 2001-02-09 | 2002-02-04 | Junta roscada tubular con hilos trapezoidales con cara de hilo abombada convexa. |
US10/470,734 US7331614B2 (en) | 2001-02-09 | 2002-02-04 | Tubular threaded joint with trapezoid threads having convex bulged thread surface |
CA002437528A CA2437528C (fr) | 2001-02-09 | 2002-02-04 | Joint filete tubulaire a filets trapezoidaux avec face de filet bombee convexe |
PL363612A PL203268B1 (pl) | 2001-02-09 | 2002-02-04 | Połączenie gwintowe rurowe |
DE60201731T DE60201731T2 (de) | 2001-02-09 | 2002-02-04 | Gewinde-Rohrverbindung mit trapezförmigen Gewindegängen mit konvex gewölbter Gewindegangfläche |
AT02701403T ATE280922T1 (de) | 2001-02-09 | 2002-02-04 | Verschraubbare rohrverbindung mit trapezförmigem gewinde mit konvex gewölbter gewindefläche |
EP02701403A EP1358421B1 (fr) | 2001-02-09 | 2002-02-04 | Joint filete tubulaire a filets trapezoidaux avec face de filet bombee convexe |
BRPI0207086-3A BR0207086B1 (pt) | 2001-02-09 | 2002-02-04 | junta filetada tubular com filetes trapezoidais com face de filete arqueada convexa. |
JP2002564293A JP4070201B2 (ja) | 2001-02-09 | 2002-02-04 | 凸状に丸めたネジ表面を有する台形ネジを使用した円管のネジ結合 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR01/01793 | 2001-02-09 | ||
FR0101793A FR2820806B1 (fr) | 2001-02-09 | 2001-02-09 | Joint filete tubulaire avec face de filet bombee convexe |
Publications (2)
Publication Number | Publication Date |
---|---|
WO2002065012A1 WO2002065012A1 (fr) | 2002-08-22 |
WO2002065012A9 true WO2002065012A9 (fr) | 2003-07-24 |
Family
ID=8859843
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/FR2002/000420 WO2002065012A1 (fr) | 2001-02-09 | 2002-02-04 | Joint filete tubulaire a filets trapezoidaux avec face de filet bombee convexe |
Country Status (18)
Country | Link |
---|---|
US (1) | US7331614B2 (fr) |
EP (1) | EP1358421B1 (fr) |
JP (1) | JP4070201B2 (fr) |
CN (1) | CN1254625C (fr) |
AR (1) | AR032421A1 (fr) |
AT (1) | ATE280922T1 (fr) |
BR (1) | BR0207086B1 (fr) |
CA (1) | CA2437528C (fr) |
CZ (1) | CZ303442B6 (fr) |
DE (1) | DE60201731T2 (fr) |
ES (1) | ES2230465T3 (fr) |
FR (1) | FR2820806B1 (fr) |
MX (1) | MXPA03006962A (fr) |
MY (1) | MY126187A (fr) |
PL (1) | PL203268B1 (fr) |
RU (1) | RU2277665C2 (fr) |
SA (1) | SA02220697B1 (fr) |
WO (1) | WO2002065012A1 (fr) |
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-
2001
- 2001-02-09 FR FR0101793A patent/FR2820806B1/fr not_active Expired - Fee Related
-
2002
- 2002-01-29 AR ARP020100314A patent/AR032421A1/es active IP Right Grant
- 2002-02-04 DE DE60201731T patent/DE60201731T2/de not_active Expired - Lifetime
- 2002-02-04 CZ CZ20032444A patent/CZ303442B6/cs not_active IP Right Cessation
- 2002-02-04 WO PCT/FR2002/000420 patent/WO2002065012A1/fr active IP Right Grant
- 2002-02-04 CN CNB028042573A patent/CN1254625C/zh not_active Expired - Fee Related
- 2002-02-04 BR BRPI0207086-3A patent/BR0207086B1/pt not_active IP Right Cessation
- 2002-02-04 ES ES02701403T patent/ES2230465T3/es not_active Expired - Lifetime
- 2002-02-04 AT AT02701403T patent/ATE280922T1/de active
- 2002-02-04 JP JP2002564293A patent/JP4070201B2/ja not_active Expired - Fee Related
- 2002-02-04 EP EP02701403A patent/EP1358421B1/fr not_active Expired - Lifetime
- 2002-02-04 MX MXPA03006962A patent/MXPA03006962A/es active IP Right Grant
- 2002-02-04 US US10/470,734 patent/US7331614B2/en not_active Expired - Fee Related
- 2002-02-04 CA CA002437528A patent/CA2437528C/fr not_active Expired - Fee Related
- 2002-02-04 PL PL363612A patent/PL203268B1/pl unknown
- 2002-02-04 RU RU2003127121/06A patent/RU2277665C2/ru not_active IP Right Cessation
- 2002-02-07 MY MYPI20020425A patent/MY126187A/en unknown
- 2002-03-05 SA SA02220697A patent/SA02220697B1/ar unknown
Also Published As
Publication number | Publication date |
---|---|
CN1489680A (zh) | 2004-04-14 |
BR0207086B1 (pt) | 2011-05-17 |
PL203268B1 (pl) | 2009-09-30 |
DE60201731D1 (de) | 2004-12-02 |
PL363612A1 (en) | 2004-11-29 |
DE60201731T2 (de) | 2005-11-24 |
MY126187A (en) | 2006-09-29 |
US20040195835A1 (en) | 2004-10-07 |
CN1254625C (zh) | 2006-05-03 |
FR2820806B1 (fr) | 2004-02-20 |
CA2437528C (fr) | 2008-06-03 |
EP1358421A1 (fr) | 2003-11-05 |
RU2277665C2 (ru) | 2006-06-10 |
US7331614B2 (en) | 2008-02-19 |
ATE280922T1 (de) | 2004-11-15 |
CA2437528A1 (fr) | 2002-08-22 |
JP4070201B2 (ja) | 2008-04-02 |
CZ20032444A3 (cs) | 2003-12-17 |
FR2820806A1 (fr) | 2002-08-16 |
MXPA03006962A (es) | 2004-05-05 |
BR0207086A (pt) | 2004-01-20 |
JP2004524483A (ja) | 2004-08-12 |
ES2230465T3 (es) | 2005-05-01 |
SA02220697B1 (ar) | 2006-12-10 |
AR032421A1 (es) | 2003-11-05 |
WO2002065012A1 (fr) | 2002-08-22 |
RU2003127121A (ru) | 2005-03-10 |
CZ303442B6 (cs) | 2012-09-12 |
EP1358421B1 (fr) | 2004-10-27 |
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