FR2539480A1 - Sealing gasket locked between tubular cast iron elements interlocking with flange and bolts - Google Patents

Abstract

Sealing gasket locked between tubular elements T1 and T2, one with a male end 1, the other with interlock 3. The male end 1 carries a weld bead 4 and, abutting against this bead, a stop ring 5 upon which a loose flange 8 bears along a spherical zone 6-7. The interlock 3 houses a radially compressed sealing washer 2. On the interlock 3, there bears a ring 13 whose external diameter is greater than that of the flange 8. Locking is obtained by assembling the flange 8 and the ring 13 by means of oblique bolts 18. Application to locking pipes and tubular connections made from cast iron and spheroidal graphite cast iron, of large diameters, for the purpose of reducing the locking forces and reducing the diametral bulk of the ring, whilst allowing angular deflections.

Description

 The present invention relates to a seal or sealing assembly of tubular elements (pipes and fittings) end male and interlocking, of the type in which the male end telescopically crosses the interlocking with interposition of a seal resilient seal compressed radially between the male end of one pipe and the interlocking of the other pipe. More specifically, the invention relates to a locked seal, that is to say provided with a locking device for preventing longitudinal relative displacement of the two assembled tubular elements.

 It is known that the pipe joints or joints of pipes can disjoin, dislodge or break under the action of longitudinal and radial forces generated by the internal pressure of the pipe or by external forces originating in the during the implementation of the pipeline, in the environmental grounds (thrust of lands when the pipes are buried, accidents and movements of grounds).

 The joints or locked assemblies of buried pipelines are used in particular at the elbows of the pipes because it is here that the pipes are subjected to the most important efforts of ## 147 ############################################################################ 'we move away from the elbows.

On the other hand, aerial or open-air ducts require locks over their entire length, that is to say not only at the elbows but also at the joints between straight elements, except if these straight elements are blocked elsewhere. , by belting, for example
Numerous patents have long known and sealed connections and locked axially by flanges and bolts at the ends of the pipes This simple mode of locking is not suitable for pipes with interlocking and male end, with telescopic assembly.

 In the case of telescopic assemblies, it is known from FR-A 2 030 109, 2 120 677 and 2 165 391 to form near the male end of a pipe a flange or circular protuberance against which comes s' apply a stop ring whose outer profile matches the conjugate profile of a counter-flange also taking support on the interlocking of the other pipe. This arrangement is satisfactory for small and medium diameters but is no longer usable from and beyond a diameter of 1000 mm because the. aforementioned forces of disengagement or unlocking and breaking which are proportional to the square of the diameter then become excessive.

 In addition, as the locked joints of the two aforementioned prior patents comprise a counter-flange which is supported both on the aforementioned stop ring mounted on the tubular element with a spigot, and on the periphery of the socket of the Another tubular element forming in a way an annular bridge between the two assembled tubular elements, it is understood that, for pipe diameters equal to or greater than 1000 mm, the diameters and thicknesses of such a bridging counter-flange become excessive. Indeed, said counter-flange must be designed to withstand radial forces and unlocking forces, in particular during the introduction of fluid under pressure into the pipe, which are proportional to the square of the diameter of the circle of application of said efforts on a bearing surface of the counter-flange. The manufacture of such a special counter flange of large diameter and high thicknesses is not envisaged for pipe diameters equal to or greater than 1000 mm.

 The present invention therefore poses the problem of creating a locked seal for tubular elements of large diameters, for example equal to or greater than 1000 mm, by taking up characteristics common to the joints of the two aforementioned patents, but by renouncing the counter-flange. which bears on both the spigot and on the joint of the joint.

 To solve this problem, the subject of the invention is a locked seal of the abovementioned type between two tubular pipe-casting elements, one with a spigot end, the other with an interlocking housing, a sealing gasket # crossed by the end male on which it is applied, of the type in which the spigot has a radial annular protuberance at a distance from its end edge, in which a rigid but radially split stop ring abuts the protuberance of the opposite side to that of the end edge of the spigot and of the type comprising locking means between a spherical zone of said stop ring on the spigot and the periphery of the socket, this seal being characterized in that has a support flange on the stop ring mounted on the. male end of a tubular element and a separate support means on the periphery of the interlocking of the other tubular element, said support flange and said separate support means being joined by oblique bolts of diverging axes relative to the axis of assembly of the tubular elements, from the spigot to the socket, the annular piece (or support means) bearing on the socket having a diameter substantially greater than that of the annular piece bearing on the stop ring (or loose flange) on the spigot end.

 According to a feature of the invention, said separate support means is applied by a bearing slope on a peripheral annular protrusion of the interlocking.

 According to another characteristic of the invention, said separate support means on the interlocking is a crown.

 According to another characteristic of the invention, said separate support means on the interlock is constituted by a number of support blocks distributed around the periphery of the interlocking and surrounded by a ring.

 With this arrangement, and more precisely by separating the support flange on the spigot and said separate support means on the nesting, and their meeting by diverging oblique bolts, the axial forces or the axial components disengagement forces exerted on the support flange on the stop ring remain within acceptable limits, even for large diameters of the tubular elements, therefore of the spigot, since the external diameter of the flange of support is substantially less than the outer diameter of the interlocking if the attachment of the bolts takes place directly on the interlocking, or a counter-support flange on the interlocking, if the attachment of the bolts s' performs indirectly on the interlocking via this counter-flange support.

 In contrast to the seals locked by bolts parallel to the axis of the pipes to be joined, which involves the implementation of flanges of diameter at least equal to that of the attachment means of the nesting that one Coupling and consequently relatively thick to allow them to withstand the bending forces perpendicularly opposed to them, the locking by oblique bolts reduces the dimensioning of these parts and therefore their lightening, minimizing the axial and radial forces to the right of the joint by virtue of the force components provided by the combination of the inclined bearing surfaces of the flanges and counter-flanges with said oblique bolts, the resultant of the generated forces being substantially in opposition to that relating to the reaction of the locking bolts. obliqueness of the support means and bolts also promotes the quality of the attachment of the counter-flange on the nesting since the re The result of the reaction of the bolts converges towards the center of the pipe thus avoiding the risk of expansion and sliding of the counter flange over the circular protrusion of the interlocking during excessive axial thrusts.

 Radial forces radial components of disengagement or unlocking forces on the support flange on the spigot are also considerably reduced compared to the case of prior patents or the bearing piece on the spigot had a significantly greater outside diameter to that of the nesting. As a result, the dimensions of the support flange on the spigot are reduced in both diameter and thickness.

 Other features and advantages will become apparent from the following description.

In the attached drawings given only as an example
FIG. 1 is a partial view in longitudinal meridian section
a locked seal according to the invention;
FIG. 2 is a view similar to FIG. 1 of the elements of the joint in
coaxial position, before assembly;
FIG. 3 is a view similar to FIG. 1 of the seal locked in
uneven position of deflection between the tubular elements;
Figs. 4A and 4B are comparative half-views in section
longitudinal diameter of a locked joint according to the invention
and an earlier locked joint, with force diagrams;
- Figs. 5 and 6 are views similar to FIG. 1 of variants of the
lock seal of the invention for tubular connectors;
FIG. 7 is a partial perspective view of a detail of a
means of support of the seal variant locked according to 7-7 of the
Fig. 6 and without bolts, nuts or washers;
FIG. 8 is a view of the elements of the seal of FIG. 6 close together
before assembly
FIG. 9 is a partial end view of the seal of FIG. 6 and
support means of FIG. 7 illustrating a distribution of resources
support on the nesting.

FIG. 10 is a small scale diagram of buried pipe
with an elbow undergoing stresses and strains during
the introduction of the fluid to be transported under pressure
- Figs. 11 and 12 are partial views of detail, to larger
scale that FIG. 4 stop ring support means and
protuberance on a male end, and efforts exerted on
these means of support.

 According to the exemplary embodiment shown in FIGS. 1, 2 and 3, the invention applies to a tight seal and locked between two ducts T1 and T2 made of ductile iron or not, axles XX brought to coincide, the pipe T1 having its male end 1 and the T2 pipe having its interlocking 3 inside which is housed an elastic seal 2 elastomer.

 On the side of the spigot 1 of the pipe T1, the male end 1 intended to be inserted into the socket 3 through the hermit seal 2 has a protuberance at a distance from its end edge. annular 4 continuous or interrupted formed for example by a weld bead ductile iron. On the weld bead 4 abuts a stop ring 5 of diameter equal to or slightly less than that of the end 1, made of rigid material, for example the same metal as the pipes T1 and T2 so preferably of ductile iron , or electrically insulating material and not corrodable.La ring 5 is slotted radially to give it some elasticity, that is to say, allow it first of all some expansion necessary during its assembly by crossing the protuberance of the cord 4 and then allow it to retract and apply tightly on the shaft of the male end 1 of the pipe T1.

 By an inclined profile in the form of a spherical zone 6 intended to ensure good contact and a good distribution of forces (see below, in relation with FIG 4A), the ring 5 is supported on a counter-profile or conjugate profile 7 of an annular flange 8. If one draws the tangent to the spherical zone 6 - 7 at a point B of mean radius of this spherical zone, this tangent Bt makes with the axis XX an angle x substantially greater than 450 In comparison with a known locked seal (Fig. 4B), whose tangent Ot makes an angle y substantially less than 45 with the axis XX, the angle x is sensi # oleren: s # r - eur at the angle y.The flange 8 has a meridian section L. The flange 8 has, equidistantly along a circumferential line and around its axis XX, a series of bolt holes 9 of oblique, divergent YY axes. that is, away from the XX axis towards the male end edge. The holes 9, slightly frustoconical, have their large diameter located on the side of the pipe joint or the side of the male end edge. Each hole 9 s flares on the side of the small diameter, therefore opposite the seal, by a spherical bearing surface 10 in which has been made, on the side of the upper generatrix of the pipe T1, a flat surface 11. The span 10 and the flat part 11 open on the inner portion of the general L-shaped profile of the flange 8. The bearing surface 10 of a bolt is oblique with respect to the axis XX of the flange 8 and is centered on the YY axis of the bolt. .

 The inside diameter of the flange 8 is slightly greater than the outside diameter of the bead 4 to enable it to be slipped onto the male end 1 before the slotted stop ring 5 is installed. The L-shaped flange 8 is designed for a casting without core.

 On the side of the socket 3 of the pipe T2, a separate support means is constituted by a bearing ring 13 of larger outer diameter than the flange 8. The ring 13 is supported on a peripheral circular protrusion 14 of the fitting 3 of the pipe T2 and faces or is opposite to the flange 8. In the extension of the oblique axes YY of the holes 9, the crown 13 with skirt 13a is perforated with frustoconical bolt holes 12 which are therefore in the axial extension of the holes 9 of the flange 8. As for the holes 9 of the flange 8, the holes 12 of the counter flange 13 have a frustoconical profile to allow their coreless casting and the deflection of the bolts. The largest diameter of each hole 12 is oriented towards the end edge of the socket and towards the holes 9, opening on the inner surface of the skirt 13a. The small diameter of the holes 12 is flared by a spherical bearing 15 on the opposite side to the skirt 13a, or, in other words, on the flaring side of the nesting bell or bell 3.

The ring 13 internally comprises a counter-profile 16 which bears on the slope 17 of the circular protrusion 14 of
the nesting 3 when the loose flange 8 abutment on the stop ring 5 and said ring 13 are joined by oblique bolts 18, of axis YY, engaged in the holes 9 and 12. The bolts 18 have a head 19 having a spherical bearing surface 20 and a flattened surface 21 intended to be fitted on the loose flange 8 in conjunction with the spherical bearing surface 10 and the flattening surface 11 of the flange 8 respectively, and having a spherical bearing nut 22 which is applied to the spherical bearing surface 15 of the crown 13.

Assembling the joint (Assembly) (Fig. 1 and 2B:
In order to seal a pipe T1 and a pipe T2 in a sealed manner, the flange 8 is first engaged on the male end of the pipe T1 with its spherical bearing surfaces 10 of bolt holes 9 facing towards the non-rigid pipe. represented by the pipe Tl. The flange 8 is threaded beyond the annular protubrance 4 in order to allow the insertion of the split stop ring 5 which is also engaged on the male end 1, while maintaining it. in elastic expansion to cross the cord 4 while it is dragged beyond the annular protuberance 4 and more exactly between this protrusion and the loose flange 8. It is then slid longitudinally on the pipe T1 the crazy flange 8 towards the edge of the male end 1 until the counter-profile 7 of the flange 8 is applied to the profile -6 of the ring 5 and pushes the ring 5 to bear on the cord 4.

The ring 13 engages by the male end of the pipe T2 (not shown) with its support profile 16 oriented towards the bearing slope 17 of the nesting 3. Then the crown 13 coaxia is moved
2 to the axis XX of the pipe 2 until the bearing profile 16 and the slope 17 come into contact. The male end of the pipe T1 is then engaged inside the elastic lining of the pipe T2 and the pipe T1 is pushed axially until the edge of its end arrives in the vicinity of a circular abutment 23 of the bottom of the socket 3 (it is possible to use, for this purpose, threaded rods passing through the holes 9 of the flange 8 and the holes 12 of the crown 13, to
the place of any other system or specific casing machine). Thus, a telescopic seal of the type described in FR-A-1 168 # 647, patent according to which the seal is formed.
is compressed radially.

The flange 8 and the support ring 13 are then joined together by
bolts 18 after matching holes 9 and 12 and blocked
in rotation the head 19 of each bolt by its flat 21 applied on
the flange 11 of the flange 8. To lock the seal, we tighten the
nuts 22.

For the uncoupling of pipes T1 and T2, the procedure is
reverse.

According to FIG. 3, the locked seal of the inven
tion has an angular deviation between the axis XX of the pipe 11,
the stop ring 5, the idle flange 8 - and the axis X1-X1 of the pipe T2
and the crown 13. The axes XX and X1-X1 make between them a small
alpha angle. Due to this deflection, the nuts 22 of the bolts 18
are closer to the head 19 on one side of the axes XX and Xl-Xl that
diametrically opposite coast.

It is thanks to the radial clearance between the male end 1 of the pipe Tl
and the bottom of the socket 3 of the T2 pipe and the elasticity of the gar
2 and thanks to the obliquity of the bolts 18, to the
combination of spherical bearings jO, - 20 and 15, and clearance
frustoconical holes 9-and 12 as well as sliding surfaces
formed by the conjugate bearing profiles 6-7 of the ring 5 and the flange 8 that an angular deflection of angle alpha is permitted at
right of the seal 2 of the T2 pipe without compromising
sealing of the seal or its locking. The angle alpha is by
example, at laying, 1.5 for large equal diameters or
greater than 1000 mm.

According to FIG. 4A, the forces proportional to the pressure
internal of the pipe T and proportional to the square of the diameter of this
the last exert inter alia an axial thrust on the limb;
3, fi 'on the flange 8, parallel to the axis XX of the pipe T, ten
to dislodge the male end 1 of the hose T1 from the embol-
3 of pipe T2.Each bolt 18, inclined along a line
oblique YY with respect to the axis XX of the pipe T1, joins the crown 13
at the flange 8, and opposes these forces fl-fl 'according to this same
line YY by forcing the flange 8 by its bearing surface 7, and the
crown 13 by its support surface 16, to apply even more
intimately on their respective bearing surfaces 6 and 17 that the forces fl and fl 'are higher.

Push on the socket 3 and on the flange 8
Due to the inclination of the bearing surface 17, the ex thrust fl on the bearing slope 17 of the socket 3 produces a radial force component f2 with a resultant f3 normal to the slope 17 which strongly urges the crown 13. The axial thrust fl 'on the bearing face 6 of the flange 8 is translated, by means of the bolts 18 which join the flange 8 and the ring 13, by a reaction r equal to fl', on the crown 13.

Reaction of bolts 18 and crown 13
Because of the obliquity of the attachment bolts 18 related to the difference in the diameters of the flange 8 and the ring 13, the bolts 18 and the ring 13 oppose said axial thrust fl-fl 'by oblique reactions following the axes YY which are respectively r3 on the ring 13 and r3 'on the flange 8 and which are decomposed into axial components r1 and r1' of lower intensity than the resultants r3 and r3 ', and in radial components respectively r2 centripetal on the ring 13 and r2 'centrifugal on the flange 8.

 For the ring 13, the centripetal radial component r2 of the reaction is subtracted from the radial component fi of thrust which significantly relieves the ring 13 and reduces the dimensioning. As for the centripetal component f4, it exerts a catching action of the crown 13 on the support slope 17 of the socket 3.

 In addition, the ring 13 undergoes twisting forces which are reduced due to the obliquity of the bolts 18 and the decrease in the section of the ring 13, which therefore allows the aforementioned dimensioning reduction.

 Subject to the same conditions of use as before, the male end 1 of the pipe T1 which tends to disengage from the interlock 3 under the effect of the axial thrusts fl fl 'exerts an axial thrust towards the flange 8 hooked to the crown 13 by bolts 18.

This force is transmitted to the bearing surface 7 of said flange 8 by the counter-bearing profile 6 of the stop ring 5 abutted axially on the circular protuberance 4 itself secured to the spigot 1. Of this thrust axial fl-fl ', it results, at a point B of the bearing surface 6, a force f3'se decomposing axial components fll parallel to the axis of the pipe Tl and exerted in the direction of de debofement of the latter and radial f2 'oriented towards the outside of the pipe. According to this distribution of force fl 'opposes the reaction rl' of the bolt 18 and f2 'is added to r2' of the same bolt, to give a resultant f2 '+ r2' centrifugal.

 In comparison with a locked seal of known type (FIG. 4B) with locking bolts 18 of ZZ axis parallel to the axis XX, the resultant f2 '+ r2' of FIG. 4A is smaller than the radial centrifugal component f2 of Fig. 48 due to the inclination y smaller relative to the axis XX of the tangent Dt to the spherical zone 6-7 at a point D (Fig. 4B) than the inclination x tangent at a point B (Fig.4A). As a result, in favor of the seal of the invention (FIG. 4A), a decrease in expansion stress of the flange 8 is observed.

The inclination of the bolts 18 on the axis XX and the corresponding obliquity of the flange 8 results in a reduction of the bending forces exerted by the bolts 18 on the flange 8. If we compare the
4A and 4B, the bending forces of the bolts 18 on the flange 8A (deformed flange shown in broken lines) of the anterior seal (FIG 4B) are substantially greater than those to which the inclined flange 8 with an oblique bearing surface 10 is subjected. This also results in a lightening of the flange 8 and the crown 13 in accordance with the comparative numerical table I which will be found at the end of the description.

 Referring now to Figs. 11 and 12 which show, on a larger scale, two embodiments of the stop ring support means 5-5a and radial protuberance on the spigot 1, we see that the radial protuberance may be constituted either by an annular weld bead 4, or by a ring 4a reported and welded by two welding beads 4b. In FIG. 11, the ring 5 comprises a transverse support on the weld bead 4 with a machined bearing transverse face.

 In FIG. 12, the ring Sa has a tapered reclining bearing 5b bearing on the weld bead 4b of the welded ring 4a.

 In both cases (Fig.ll and 12) the Ring Set ring Sa have a cylindrical bearing surface of width 1 on the spigot 1 which is for example of the order of 1/20 of the outside diameter of the barrel 1 .

In both cases, the ring 5 and the ring Sa have a tangent Bt to the spherical contact zone 6-7 with the flange 8 which is at an angle x with a generatrix of the spigot 1. This angle x is greater than 45.

 If one traces the resulting force f5 'of support of the flange 8 on the ring 5, this force f5' passes substantially below or behind the point A or the contact point Al of the radial protuberance 4 or 4a. 4b with the outer wall of the spigot 1.

 The torque constituted by the force f5 'with respect to the point A or Al tends to apply the stop ring Sou Sa to the barrel 1 of the pipe and not to tilt it on the other side of the radial protuberance 4 or 4a -4b.

This is therefore a locking security since any risk of crossing the radial protuberance 4 or 4a-4b by the ring 5 is discarded. In addition, this allows a constrictive force f4 '(in correlation with a large width 1, which decreases the specific pressure on the barrel 1), which relieves the protuberance 4 or 4a-4b of its axial locking force or retaining of the ring 5 or Sa
The increase of the stress con # stricteur f4'- advantageously increases the friction force of the ring 5 on the barrel, which is favorable to the desired locking (this friction force is the product of the constraint force f4 by the coefficient of friction of the material of the ring 5 on the cast iron of the barrel 1). In accordance with the variant of FIG. 12, the annular protuberance 4a 4b is even more relieved in its axial locking force by the recessed frustoconical bearing surface 5b. of the stop ring Sa since the support, transverse axial thrust force of Fig.ll is replaced by an oblique support undergoing an inclined support force which is decomposed into a centripetal radial component to the barrel 1 and an axial component weaker than said axial bearing force of FIG.

 Finally, in comparison with an earlier locked joint, the width range 1 (FIG. 4A) of the ring 5 on the barrel 1 is greater than that (FIG. 4B) of the ring 5 of the front seal.

 According to FIG. 4A (seal of the invention), the reaction of the flange 8 on the stop ring 6 produced by the common spherical bearing zone 6-7 of the equal and opposite radial forces F4 'constrictors. centrifugal radial forces ~ 2 '. However, despite the relative weakness of the thickness of the pipe T1 relative to its large diameter, the value of the angle x of the tangent Bt to the bearing surface 6 and the width 1 of the ring S are such that the pipe it is locked axially with the pipe T2 without throttling, during heavy efforts, the barrel 1 of the pipe T1 to the right of the stop ring 5 subjected to the strong f4'.Cette value angle x greater than 450 further reduces the risk of diametric expansion of the profile 7 of the flange 8 under the wedge effect exerted by the stop ring 5 according to its profile 6. The risk of crossing the ring of stopping 5 by the flange 8 is therefore also reduced. In other words, the value of the angle x of the bearing surfaces 6-7 is a compromise between the desire to exert an axial bearing force on the ring 5 and the desire to increase the constrictor force f4 'on the shaft 1 which axially relieves the radial protuberance 4 or 4a-4b by decreasing said axial bearing force on the ring 5.

 Whereas, in the preceding case, the invention applies more particularly to the junction of two pipes end and mating end, the variant of the invention which follows applies mainly to the junction between the end male of a pipe T3 with the interlocking of a connection R1 having for example a socket at each end, which prohibits the use of a ring 13 in one piece.

 According to the embodiment shown in FIG. 5, the equipment of the pipe T3 is strictly identical to that of the pipe T1 of the preceding example of FIGS. 1 to 3, that is to say, arranged in the same manner, the following elements of locked joints # and according to same references: a male end 1 of a pipe T3 is provided with a continuous or discontinuous annular protuberance 4 in the form of a continuous weld seam or not. On the cord 4 abuts a split stop ring 5 whose peripheral profile 6 is pressed against the counter-profile 7 of an idle flange 8. The flange 8 has frustoconical holes 9 of axes YY divergent with respect to its axis XX away from the axis XX to the male end edge or to the seal or to the fitting of the connection Rl. The holes 9 are intended to receive head bolts 19 with spherical bearing 20 and flattening 21 fitting into the respective recesses of the holes 9 with spherical bearing surface 10 and flattening 11.

 On the side of the fitting 3 of the connection R1- of axis XX which has another socket 3 at the other end, there is found the seal 2 housed in the socket 3 in which is embodied the male end 1 through the pad 2.

 This variant R1 connection according to the invention differs however in that, in replacement of the ring 13, the separate support means is a flange 141 increasing the protuberance or peripheral projection of the socket 3 and belonging to the connection R1 ..

The flange 141 comprises a series of frustoconical holes 121 of oblique YY axes, equidistributed about its axis XX at the same inclination on the axis XX as the axes YY of the flange 8, and from a small circle b of diameter greater than that of the circle has a larger diameter by which the YY axes out of the idle flange 8. Each diverging axis YY holes 121 of said flange 141 is aligned, during assembly of the seal, exactly in the extension of the YY axis of the corresponding hole 9 of the loose flange 8 to merge and form a single axis YY.

 The connection between the loose flange 8 of the pipe T3 and the flange 141 of the connection R1 is ensured by bolts 18, each of these bolts traversing obliquely, along an axis YY, a hole 9, then the hole 121 opposite it, and thus concretizing the alignment of the holes 9 and 121.

The locking of the seal is ensured by the tightening of the nuts 22 screwing on the bolts 18 and bearing on the bearing slope 171 of the flange 141 via an elastic device capable of compression which may be for example a washer or a set of metal washers 24 of the kind "Belleville". Such an elastic device serves to absorb the large bending forces due to the pressure of the fluid transported during the pressurization of the pipe (see Fig.10 or the deformation of the pipe is shown in broken lines in R2a and Ta).

 To assemble and seal a seal locked on a pipe T3 and a connection R1, the procedure is the same as in the example of FIGS. 1 to 3 starting by equipping the pipe T3 with its flange 8 and its stop ring 5.

 This variant allows additional angular deflection of the angular deflection at the laying. The additional deflection is a few tenths of degrees to the right of the seal 2 of the socket 3 and is obtained without altering the seal of the seal. Thanks to the flexibility of the elastic lining 2 still remaining after locking the seal by the nuts 22 and partial compression of the washers 24, the conjugation of the profiles 6 and 7 serving as a ball joint, and thanks to the light play still remaining between the spigot 1 of the pipe T3 and the walls of the axial abutments 23 and of the inner concentric chamber of the socket 3 at this level, the washers 24 absorb the large bending forces P and Q to the right of the joints II (FIG. to break the flange 141 or the locking elements, in particular the protuberance 4, these forces P and Q (FIG. 10) originating either in the pressurization of the pipe, and in particular manifesting itself in an elbow R2 of the pipe which tends to deform in R2a (Fig.10) 9 is a thrust of ground constraining the angle alpha (Fig. 3) of deviation to the pose to close or to open beyond or below the angular value locked to said pose. (These are, of course, buried non-stop pipelines at the joint locations while the overhead lines are abutted at the joint locations).

 The additional angular deflection, which cancels the bending moments due to the external forces, also allows a good distribution of the forces on the various elements of the locked joint which are the protuberance 4, the ring 5, the flange 8, the flange 141 and the bolts 18.

 As a variant, not shown, it is of course possible to use washers 24 in the example of FIGS. 1 to 3.

 According to another variant of a locked seal (FIGS.6 and 7), the invention applies to the assembly of two pipes with a male end and a socket, or to the assembly of pipes with a male end and a fitting having at least one interlocking. This variant has the advantage of using the socket as such as locking support, as in FIG. 1, without external modification in the form of flange 141 or other, and without using a ring 13 to be threaded through the other end, that is to say by the male end of the fitting or pipe but using another separate means support.

 According to the invention, the locked seal of FIGS. 6 and 7 assembles a T4 pipe and a connection R2. The pipe T4 is equipped according to the means and methods used for the pipes T1 and T2 of the preceding examples (Fig. 1 to 5) and of a connection R2 or a pipe carrying a nesting.

In the following description, we will take the same benchmarks as before whenever there will be similarity between elements and we will limit the description to novelties and features compared to previous examples.

 The ring 13 is replaced by small parts or shims 131 and a ring 26 constituting said separate support means.

 On the circular protuberance 14 with bearing surface 25 and on the support slope 17 of the socket 3 of the coupling R2 of axis XX, the bearing surfaces 161 and 28 of a number of parts or support blocks 131 distributed around the circular periphery of the surface 25. Their number is a function of the forces related to the internal pressure of the fluid transported and the distance of the seal locked to the tubular change of directional elbow. The bearing surfaces 161 are similar to the bearing surface of the ring 13 of FIG. 1. Each wedge 131 has a hole 122 inclined relative to the bearing surface 161 so that, on the assembled joint, the YY axis is oblique and diverges from the end edge 32 of the interlocking 3 to the flaring of the bell or socket tulip.On the assembled joint, the YY axis is fixed and materialized by a bolt 18 carrying a nut 22 and possibly metal washers 24 with elastic compressibility to limit and better restart the tightening efforts. The parts or wedges 131, hollowed out by the frustoconical bolt holes 122, and their flares, have an external bearing surface 27 constituted by a frustoconical portion.

 The bearing blocks 131 are held in the bearing position on the surface 25 of the socket 3 by a belt or ring 26 whose inner surface 29, frustoconical, is conjugate of the frustoconical portion 27 belonging to each block 131. small diameter of the frustoconical surfaces 27 and 29 of the wedges 1-31 and the ring 26 is in the assembled joint, on the side of the flaring of the bell or socket tulip 3 and the large diameter of said frustoconical surfaces is on the side of the end edge 32 of the interlocking.At regular intervals, of width 1, corresponding to the width 1 of the surface 27 of each shim 131, the inner surface 29 of the ring 26 is staked, all over its circumference, inner bosses 30 abutment and guiding shims 131 which allow 1-attral holding said wedges and their judicious distribution (Figure 9) on the protuberance 14 and its peripheral surface 25 depending on the forces to bear. In other words, the inner surface 29 of the ring 26 constitutes with its internal bosses 30 an internally castellated surface.

Thus, if the forces are unevenly distributed around the perimeter of the engagement 3, it is possible to concentrate shims 131 and their bolts 18 in a zone of high tension and disperse them in small numbers on the diametrically opposite zone, or the voltage is low.

The frustoconical support surface 29 of the belt 26, combined with the bearing surface 27 of the wedges 131, also allows, in addition to its participation in the plating of the wedges 131 against the bearing surfaces or bearing surfaces 25 and 17, the catching up execution tolerances of the various parts entering the composition of the joint, in particular of the interlock 3, the shims 131 and their bolt holes 122,
The assembly of this seal is made, male side of the pipe T4 as in the previous examples. On the interlocking side 3, the crown 26 is firstly coaxial with the axis XX of the connection R2, the large diameter of its frustoconical inner surface 29 faces the edge 32 of the socket 3, and the ring 26 is threaded onto the nesting 3 to place temporarily support (Fig. 8), by its own weight, on the upper generatrix of the shaft of the connector R2 behind the interlocking, thus temporarily losing its coaxiality with the connection R2. The male end of the pipe T4 bearing its ring 5 and its flange 8 is then introduced into the lining 2 of the socket 3 according to the method already described in the previous versions, then it is associated with the flange 8, using a bolt 18 and a nut 22, and washers 24, if necessary, a first support wedge 131 with the loose flange 8 opposite it, the bearing surfaces 28 and 161 of said wedges coming from conjugate with the bearing surfaces 25 and 17 of the interlocking 3. Note that this operation will be facilitated that we choose the upper generatrix of the interlocking 3 for the assembly of the first block 131. Then we reconcile and the seat belt 26 is supported by its own weight on the wedge 131 by arranging for the crenellated bearing surface 29 of the belt 26 to come together or somehow to interlock between two bosses 30 on the bearing surface 27 of the hold 131. To prevent slippage inadvertent belt 26 on the support wedge 131 during the following operations, it can provisionally ensure the maintenance of the belt 26 by adhesive means or welding means at the contact plane of the bearing surfaces 27 or 29, preferably on the opposite side to the joint plane, that is to say on the side of the small diameters of the surfaces 27 and 29 which are opposed to the interlocking wafer 32. A second shim 131 is then inserted between the surfaces 25 and 29 preferably using the slot between the bosses 30 which is diametrically opposite the slot occupied by the first shim 131 used, and then this second wedge 131 is connected to the idle flange by a bolt 18 which is deputy washer 24 possibly and then a nut 22 that is screwed without tightening. The other shims 131 are then mounted according to the same process, step by step, then, by pushing the ring 26 towards the pipe T4, that is to say in the direction of the arrow f of the
Fig.6 of the small diameter to the large diameter of the surfaces 27 and 29, the wedges 131 are locked on the supports 28 and 161, thus producing a wedge effect, and uniformly tightened the nuts 22.

 In the same way as the two previous examples, this third example of a locked joint according to the invention allows angular deviations between the pipe T4 and the connection R2 of the order of 1.5 ", this deflection being allowed by the radial clearance between the male end 1 and the bottom of the socket 3 as well as by the elasticity of the seal 2.

 Again, this third example has the advantage of being able to unequally distribute the oblique bolts 18 on the periphery of the interlocking 3, depending on the location of the unlocking forces to which the seal must resist.

In addition, this third example with recessed wedges 131 has the following advantage in the case of a pipe buried in a S # S having a bend R2 (Fig.10): it was written at the beginning that, when setting in pressure of the pipe, it is the elbow R2 which is subjected to the most important thrust forces (force P at the elbow and forces Q on the locked joints J1 between the elbow R2 and the coupled pipes T) and that the forces decrease as one moves away from the elbow R2.This means that the successive joints J2, J3,
J4, etc ... between straight elements or pipes T of the pipe, on either side of the bend R2, are subjected to unlocking efforts of less and less high and that, therefore, it can reduce the number of shims 131 and corresponding bolts 18 on the joints J2 with respect to the locked joints J1, on the joints J3 with respect to the joints J2, etc. In other words, this third example has the advantage of offering a modular locking seal or adaptable or adjustable, that is to say, increasingly light as we move away from the elbow R2, as shown in the digital table (II) presented at the end of the description.

 But also, whether the bolts 18 are uniformly distributed or not around the periphery of the interlocking 3, this third example has the advantage, compared with the previous examples, of providing a support means (26-131) on the 3, lightened compared to the previous examples since the hollow wedges 131 are few, and are far from filling the entire annular space between interlocking 3 and crown or belt 26.

 Alternatively, finally, one can mount the ring 13 on the socket 3 of a two-socket connector by a balancer attachment system.

 See numeric tables I and II on the following page.

TABLE I (Fig. 4A - ssB)
Weight comparison of the flange 8 and the crown 13 for a 1400 mm diameter pipe.

- In the case of the invention (Fig. 4A): Locked bolted joint 18
obliques.

- In the case of the known technique (Fig. 4B): Joint locked to
bolts 18 parallel to the axis of the pipe.

<Tb>

: <SEP>: <SEP> Bolts <SEP> 18 <SEP>: <SEP> Bolts <SEP> 18 <SEP>: <SEP> Lightening <SEP> or <SEP> gain
<tb> oblique <SEP><SEP>:<SEP> parallel <SEP> to <SEP> :: ----------: ---------: <SEP>
<tb> the axis <SEP><SEP>:<SEP>
<tb>: <SEP>: <SEP> (Fig. <SEP> 4A) <SEP>: <SEP> (Fig. <SEP> 4B) <SEP>:
<tb> kg <SEP>: <SEP> kg <SEP>: - <SEP> kg
<tb>: <SEP> Flange <SEP> 8 <SEP>: <SEP> 250 <SEP>: <SEP> 312 <SEP> - <SEP>: <SEP><SEP> 62 <SEP>: <SEP> 20
<tb>: <SEP> Crown <SEP> 13 <SEP>: <SEP> 190 <SEP>: <SEP> 204 <SEP>: <SEP> 14 <SEP>: <SEP> 7
<tb><SEP> Set <SEP> Without <SEP>: <SEP>: <SEP>: <SEP>: <SEP>: <SEP>
<tb><SEP> the <SEP> bolts <SEP> 18 <SEP>: <SEP> 440 <SEP>: <SEP> 516 <SEP>: <SEP> 76 <SEP>: <SEP> 15
<Tb>
TABLE II (Fig. 6 10)
Lightening the Locked Joint of the Invention of FIGS. 6 to 10 with respect to a locked joint -contrebride and bolts next
FR-A 2,165,391.

NB- The equivalent operating pressure is the effective pressure
internally to which the locked joint is requested following
the internal angle of the elbow of the pipe (the more the angle is
low, the stronger the stress) and the distance
seal relative to the elbow.

<Tb>

: <SEP> ~ <SEP><SEP>.<SEP>.<SEP>.<SEP>:<SEP> Loss <SEP> (-) <SEP> or <SEP>:
<tb>: <SEP>: <SEP><SEP> pressure: <SEP>: <SEP>: <SEP>: <SEP> Set <SEP>: <SEP> gain <SEP> (+) <SEP>:
<tb><SEP>:<SEP> Counterbrid <SEP>: <SEP> of <SEP> Service <SEP>: <SEP> Crown <SEP> 26 <SEP>: <SEP> Shims <SEP> 131 <SEP> : crown <SEP> 26 <SEP> by <SEP> report <SEP> h <SEP>
<tb>: <SEP> FR-A <SEP> 2 <SEP> 165 <SEP> 391:. <SEP><SEP> equivalent <SEP>: <SEP>: <SEP>: <SEP> + <SEP> shims <SEP> 131 <SEP>: <SEP> counter flange <SEP>:
<tb>: -----------------: -------------: -------------- -: ---------------: <SEP> ---------------: <SEP>
<tb> kg <SEP>: <SEP> bar <SEP>: <SEP> kg <SEP>: <SEP> number <SEP>: <SEP> kg <SEP>: <SEP> kg <SEP>: <SEP > kg
<tb>: <SEP> 210 <SEP>: <SEP> 16 <SEP>: <SEP> 120 <SEP>: <SEP> 36 <SEP>: <SEP> 100 <SEP>: <SEP> 220 <SEP >: <SEP> - <SEP> 10
<tb>: <SEP> 210 <SEP> 14 <SEP>: <SEP> 120 <SEP>: <SEP> 32 <SEP>: <SEP> 90 <SEP>: <SEP> 210 <SEP>: <SEP > 0
<tb>: <SEP> 210 <SEP> 10 <SEP>: <SEP> 120 <SEP>: <SEP> 24 <SEP>: <SEP> 67 <SEP>: <SEP> 187 <SEP> + <SEP > 23
<tb>: <SEP> 210 <SEP>: <SEP> 5 <SEP>: <SEP> 120 <SEP>: <SEP> 12 <SEP>: <SEP> 34 <SEP>: <SEP> 154 <SEP >: <SEP> + <SEP> 56 <SEP>:
<Tb>
Due to the modularity of the seal, that is to say the adaptation of the number of bolts to the equivalent service pressure - see Table I -, the relief is 4.5 kg per bolt less, or 50 kg for an equivalent pressure of 10 bar, and 100 kg for an equivalent pressure of 5 bar.

Claims (18)

 1.- Locked seal between tubular elements of cast iron pipe, one with spigot (1), the other with socket (3), housing a resilient seal (2) through which the spigot passes (1) on which it is applied, of the type in which the spigot (1) has a radial annular protuberance (4, 4a) at a distance from its end edge, wherein a stop ring (5, 5a) rigid but radially split is in abutment on the protuberance (4, 4a) on the side opposite to that of the end edge of the spigot (1), and of the type comprising locking means between a spherical zone of said ring stopper (5, 5a) on the spigot (1) and the periphery of the socket (3), this gasket being characterized in that it comprises a bearing flange (8) on the ring stopper (5, 5a) mounted on the spigot (1) of a tubular element and a separate support means (13-141-26-131) on the periphery interlocking with the other tubular element, said support flange (8) and said separate support means (13-141-26-131) being joined by oblique bolts (18), axes (YY) diverging with respect to the axis (XX) for assembling the tubular elements (T1, T2), from the spigot (1) towards the socket (3), the annular piece (13, 141, 26, 131) bearing on the interlock (3) having a diameter substantially greater than that of the annular piece (8) which bears on the stop ring (5, 5a) and which is a flange mounted crazy on the spigot (1).  2.- Locked gasket according to claim 1, characterized in that the separate support means (13-141-26-131) on the interlocking (3) is applied by a support slope (16 17-161-171-28) on a peripheral annular protuberance (14-141) of the embo - ment (3).  3.- Locked seal according to claim 1, characterized in that the separate support means on the interlocking (3) is a ring (13).  4.- Locking gasket according to claim 1, characterized in that the separate support means on the interlocking (3) is, in the case where the tubular interlocking element (3) is a connection (R1 ), a flange (141) increasing the peripheral protrusion deltembementement (3).  5.- Locked seal according to claim 1, characterized in that the separate support means on the interlocking (3) is constituted by a number of support blocks (131) distributed around the periphery of the interlocking (3) and surrounded by a crown (26)  6. Seal according to claim 1, characterized in that the separate support means (13-141-26-131) on the embol- ment (3) has an outer diameter substantially greater than that of the support flange (8) on the stop ring (5, 5a) mounted on the spigot (1).  7.- Locked gasket according to claim 1 characterized in that the oblique bolts (18) joining the flange (8) and the separate support means (13-141-131-26) through said flange (8) and said separate support means (13-141-131) by frustoconical bolt holes (9, 12, 121, 122) whose large diameter is opposite and the small diameter is located at the opposite ends, said small diameter flaring in spherical bearing surfaces (10, 15).  8.- Locked gasket according to claims 1 and 7, characterized in that the bolts (18) have a head (19) and a nut (22) whose supports are spherical and correspond to spherical bearings (10, 15) on the flange (8) itself taking support on the spigot (1), and on a ring (13) bearing on the interlock (3).  9.- Locked gasket according to claim 1, characterized in that at least one member (24) with elastic compressibility is interposed between the support piece (141-131) on the interlocking (3) and each nut (22) of a bolt (18).  10.- Locked gasket according to claim 5, characterized in that each wedge (131) has a frustoconical bearing surface (27) cooperating with a conical frustoconical bearing surface (29) of the crown or belt of support (26), the large diameter of this frustoconical bearing surface (27, 29) being on the side of the end edge t32) of the socket (3) or the end of the other pipe (T4) )  11.- Locked gasket according to revendicati-on 5, characterized in that each shim (131) is recessed by a frustoconical bolt hole (122) followed by a flare.  12. Seal according to claim 5 characterized in that the frustoconical bearing surface (29) of the ring (26) has at regular intervals corresponding to the width of the wedges (131) internal bosses (30). stop and guiding circumferential wedges (131) and thus provides an internally crenellated appearance.  13. Locked seal according to claim 5, characterized in that the wedges (131) are regularly distributed over the entire periphery of the interlocking (3).  14.- Locked gasket according to claim 5, carctérisé in that the wedges (131) are unequally distributed around the periphery of the interlocking (3), being concentrated in greater numbers in a zone of high tension and dispersed in a smaller number on the diametrically opposite peripheral zone of the socket (3) where the voltage is low.  15.- sealed gasket according to claim 1 characterized in that the spherical zone (6, 7) of support of the locking means on the stop ring (5, 5a) admits at a point (B) of mean radius of this spherical zone (6,7) a tangent (Bt) forming with the axis (XX) of the male end (1) an angle (x) substantially greater than 450  16.- seal-locked according to claim 1 characterized in that the stop ring (5) has a width (1), measured parallel to the axis (XX) of the male end (1) on which it is applied, which is of the order of 1/20 of the outside diameter of the barrel (1), that is to say of the male end (1-).  17.- Locked gasket according to claim 1 characterized in that, in the c.as where the radial annular protuberance (4) is a ring (4a) welded to the barrel (1) by welding beads (4b) ) the stop ring (5a) comprises a tapered bearing surface (5b) bearing on a weld bead (4b) of the stop ring (5a).  18.- Locked gasket according to claim 1, characterized in that the support flange (8) on the stop ring (5, 5a) provides the bolts (18) with a bearing surface (10). oblique to its axis (XX).