LT3250B - Fastening device for hermetic joining of pipes and hermetic telescopic join of pipes - Google Patents

Abstract

Composite seal for locked assembling of a first pipe T1 having a socket 15 and a second pipe T2 having a male end 20. The seal G comprises locking inserts 7 with a spur 11 for biting into the male end 20. The inserts 7 can undergo an angular deflection in which their inclination varies with respect to the axis X-X of the seal G. Application to the locking of pipes manufactured with large diametric tolerances. <IMAGE>

Description

The present invention relates to a fastening device for hermetically sealing pipe ends by locking coaxially telescopically connected pipes.

The present invention relates to the above-mentioned fastening device, the elastic body of which has a certain number of liner-latches at one end of the pipe to be connected, with respect to the other pipe end of the sleeve, and the device being mounted radially between the two ends.

The locking lugs mentioned in this design, made of a solid material, bend at a certain angle between the ends of the two tubes.

This design stops the axial displacement of one of the pipes to the other, which could degrade or even completely dismantle the airtight joint due to the axial forces generated by the liquid products in the pipes.

The proposed installation is more economical compared to the expensive pipe connection system in sewage systems built on deep subsoil foundations.

From French patent no. No. 1490680 discloses a known sealing fastener having liners as well as a telescopic fastening lock of the type in question. According to the present invention, each liner with a fixed and low slope for the respective axis of the device or adjustable at a small slope range by means of a hole at the end of the tube in the sleeve is secured behind the annular projection made at the thin tube end. According to an embodiment of this known method of the device, each insert is made as a plug screwed into a nut submerged in the device to adjust the useful length of said pin in the case of inaccurate coaxial connection of large diameter pipes.

Because of the small slope of said liners at the required end of the support pipe sleeve using the annular passage, and also because of the small range of angular deviation of said liners, the permissible deviations of pipe sleeve end diameters at such joining are also small.

The object of the invention is to guarantee the insertion of each liner at the end of the pipe sleeve without making an annular groove therein and without efficiently securing the liner with maximum diameter deviations at the end of the sleeve.

Such an object is achieved by using the device described in the present invention.

Thus, the object of the present invention is a device for hermetically sealing pipe ends in accordance with the essential features of claim 1.

Due to the possibility of angular deviation with respect to the mounting axis, each submerged insert therein can be matched to a diameter change at the end of the sleeve, called a tolerance for diameter. y. with an uneven ring gap between the end of the coupling and the smooth end of the connecting pipes for optimum arch fit. In this way, it is sufficient only to optimally determine the length of the liner, depending on the tolerance on diameter, in order to secure the pipe ends to each other.

Furthermore, the present invention relates to a telescopic sealing device by means of a fastening device mentioned above for locking the ends of tubular pipes to be connected with a locking device of the EN 3250 B, having the characteristics described in claims 8-10.

Thus, in order to guarantee a minimum annular space between the ends of the connecting pipes, said liner is made of a short length and, for providing such a large annular space, they have a large length. This is achieved thanks to the optimum slope of the liner rotating about an imaginary first axis of rotation for the respective end of the sleeve tube for the first set of tolerances, and around the second imaginary axis for the second set of tolerances.

ADVANTAGES AND DRAWINGS Other features of this device are illustrated in the following description, which is provided by way of illustration only and is not intended to limit the scope of the present invention. The drawings show:

Figure: Partial vertical section of the proposed device;

Figure 2-1: Partial view of this unit, Figure 2-2;

Fig. 1: inset in vertical projection at enlarged scale relative to Figures 1 and 2;

4A and 4B. Fig. 2 is a vertical sectional view / reduced scale of the two connecting pipe ends and the device itself according to Figs. 1 and 2 / respectively before and after the use of the proposed device;

Figures 5, 6, and 7: Partial vertical sections in large scale showing various positions of the liner for various ends;

Figure: Large different coupling ga.;.:

for various circular touch point graphs, and what is the slope of the liner

For the purposes of the present invention, p is a sectional view, in section, of a massive annular material and elc. Elements 1 and 2 are separated by an internal annular groove at an internal angle pusės-Χ of the side of the element 2. Small goes towards the axis Χ-Χ i 20 minimum size.

The device according to the present inserts 7 of text "Material, example, cos. Inserts 7: The circumference of the device, the large, almost elongated element 30 of the transverse angle profile of the device, the corners a and ai 9 and the markings affixed to the ring and the elastic material ε 10 give 35 in the groove 4?

For the gaps between the tubes, the ridge pattern shows the slope response of the case to the rips, as well as the gent values of the various diameters of the liners at each end of the drawing. 1, this unit nija-Χ. In its vertical member 1, the elastomeric annular support 2. to the outer grooves 3 and 4. The groove 4, separated from the edges 5, by a sizing flexible edge 5, has an internal diameter sample of a number 1 or a very solid cast metal alloy or of which one consists of a rectangular element 8 with a curved rectangular cutting head 9 and forming two obtuse with respect to the bending mandrel 9. Each part of each element 10 not in groove 3 and covered: amos 2. Spike 11 and half of inner axis of element Χ-Χ

The groove 4 has a sloping flange abutting the element 1 and a sloping flange formed by a rib 5. There are two spaces 12 and 13 between the insert 7 and each of these flanges.

The device provided with the insert is intended to be placed between the connecting end pipes T1 and T2, for example, of cast iron with ball graphite. One of the connecting tubes T1 with the coupling sleeve Fig. 15/4 has a cylindrical chamber 16 for rotating axially from the base to the sleeve inlet 15 to tilt the end of the other tube T2, a ring support 17 protruding above the chamber 16, a ring chamber 18 for support 2. also a ring-shaped entrance curb 19 defining the chamber 18 with a significantly smaller internal diameter than the support 17. The curb is connected to the chamber 18 by a rounded surface 14.

A second tube T2 with a cylindrical thin end 20 is made with allowable diameter deviations corresponding to a maximum outer diameter d2, an average outer diameter d3, and a minimum outer diameter d4. Pipes with diameters d3 and d4 are marked in Fig. 4B. T3 and T4.

When installing pipes Tl and T2 Fig. 4A. identified and aligned on a common axis Χ-Χ (Fig. 4A)

The device according to the present invention is inserted into the end of the tube T1 nipple, furthermore, the element 1 is inserted into the chamber 16 and the support 2 is placed in the annular chamber 18; the axis X coincides with the axis T1 and T2 of the tubes.

Thereafter, the thin end of the tube is introduced through the device according to the present invention, initially by bending a rib 5 which fits with some pressure against the outer surface of the thin end. As soon as the latter cuts through the edge of the liner 7, it moves into the annular gap 12 towards the element 1. The insertion of the thin end 1 continues until its outer edge rests on the base 16 of the chamber. Thereafter, the end 20 is retracted axially backward so that the inserts 7 return. the inserts change their inclination to the axis Χ-Χ due to backward angular displacement and small amplitude in the gap 13 at the annular edge 5. From this retraction, the spikes 11 of the inserts 7 engage with the outer surface of the thin end 20 and significantly impede its further axial movement. The interlocking telescopic fixing of the tubes T1 and T2 ends there.

The operation of the proposed installation, depending on the tolerances for pipe diameters, is described below.

Depending on the angular deflections, by connecting the tubes T1 and T2, each liner 7 receives a support and various inclinations depending on the diameters d2, d3 and d4.

At a minimum diameter d4, when there is a maximum annular space j4 between the end 20 and the nipple end chamber 18, the spike 11 contacts the end 20 at a given point K and the head 9 rests on the chamber 18 at only one point C. for supporting the interaction force F between the insert 7 and the thin end 20 passes through an imaginary axis of rotation R2. In this case, the liners 7 have the greatest inclination to the axis Χ-Χ, and the pipe ends are still well fixed.

For a maximum diameter d2, with a minimum annular space j2 between the end 20 and the chamber 18, the spike 11 contacts the end 20 at a certain point of engagement D, and the head 9 rests on the chamber 18 at the two points A and B.

The perpendicular intersections at points A and B denote a particular axis Rl more distal to the surface 19 than the axis R2, and the line segment joining it to the point D serves as a support for the force displacement F. In this case, the liner has the least inclination to the axis. -Χ, which guarantees reliable locking of the thin tube end.

z

Between these two extreme variants is possible a characteristic mean diameter d3, which guarantees an average annular gap j3 between the end 20 and the chamber 18; in addition, the spike 11 contacts the end 20 at a certain point H, and the head 9 rests immediately on the rounded surface 14, extending the incoming curb 19, and into the chamber. In this case, the inclination of the insert 7 has the mean value between the two values in the cases examined above.

As shown in Figures 5 and 6, this transition point is expressed as the size of the angle α2 between the line joining the axis R1 and the tip end 11 and the surface of the head 9 from the side 18 of the chamber.

According to these three cases, to ensure optimal blocking of the pipe ends, the magnitude of the reaction x, equal to the angle of the repulsive force F and the perpendicular to the end 20 at the point D, H, or K, should material of tubes T1 and T2 and the surface condition of these tubes.

To ensure blocking of the thin end 20 of the tube T2 with respect to the sleeve end 15 of the tube T1, it is necessary that the insert 7, acting on the head 9 into the chamber 18, exerts a retraction force F on the end 20. with the imaginary axis of rotation R1 and R2.

The reaction force F forms an angle x perpendicular to the base 20 at D, H, or K.

In the case of an elevated angle x, the component parallel to the force F axis jėgos-Χ predominates, perpendicular to the axis Χ-Χ, which increases However, for any end of the spigot 11 tubes, in any case, the coupling with the surface is necessary with respect to; theoretically, blocking reliability by providing an effective exterior response force F of the thin end 20 does not exceed a defined maximum limit beyond which the liner 7 does not engage beyond the outer surface of the end 20 but merely slides therein.

Conversely, at a low angle x ′, the horizontal force component F becomes very small relative to the component perpendicular to the axis of the thin end; more precisely, if the spike 11 effectively engages with the surface of the end 20, then the force F cannot significantly resist the pressure T1 of the tube T2 relative to the axis Χ-Χ and therefore does not resist reverse movement.

Fig. the letters M and L show the other points of contact of the spike 11 with the outer surface 20 of the tip 20 at diameters larger than d3 and smaller as d4, respectively. Theoretically, the axes R1 (in the case of the head 9 having two supports A and B in the chamber 18) and R2 (only in the case of one support C) are the zones where the centers of rotation of the inserts 7 are angled when the locking end 20 is tilted. connecting R1 and R2 to the various points of contact of the spike 11 with the end 20, D, H, K, M and L, are provided to support the force F in the insert 7.

The curve z joins all 11 points of contact on the spike

D, H, K, M, and L with an outer end surface 20, the diameter of which varies with technological deviations, respectively.

The curve y represents the change in the tangent to angle x / tgx /, respectively, from the tolerance of the pipe end 20 diameters, t. y. from the size of the annular gap j2, j3 and j4. This curve shows two sudden changes in direction si and s2 located near the diameter d3. It should be noted that tgx need not be equated to a coefficient of friction.

Thus, as soon as the annular gap is reduced, i.e.. y. as the diameter of the tip 20 increases, tgx and hence the value x increases to the point S2. This is true for the diameter values passing through the point SI and the diameter d2 corresponding to the minimum gap j2. However, tgx decreases between points S2 and SI. This corresponds to a certain intermediate phase in which the liner 7 no longer has a single point of contact with the outer surface of the thin end of the tube C but does not yet have an abutment point A in the incoming curb 19 and abutment point B in the chamber 18. a point B in the chamber 18, further having a support point A on a rounded surface 14. In this case, the perpendicular at the point of contact A is not parallel to the perpendicular to the entrance curb 19; this shifts the position of the axis and hence the reaction force angle χ. This case is shown in Fig. 6.

Fig. the projection of the thin tube end 20 is denoted by tgx values in the range 0.4 to 1. The projection of the y point of each curve into such a composite yields a value of tgx from which the value of x can be derived for such a diameter of the end 20.

io

For example, for points D, M, and K, the curve y has tgx values greater than 1 / at x = 46 ° /, respectively, between 0.7 and 0.8 / at x = 37 ° /, and between 0.5 and 0.6 / at x = 29 ° /.

For comparison, the dotted line shows the rotational radii of a known type of liner according to the aforementioned French patent no. 1490680 and the points N, Q and H of said insert on the thin ends of the tube of various diameters.

The rotational beams passing through a single axis R2, since there is only one point of contact between the liner and the sleeve, are marked by the reaction forces acting on the thin end of the liner.

The zl curve connects the points N, Q, and H. The dotted curve yl also has the values of tgx for this solution. It can also be seen that the angular inclination of the insert according to French patent no. 1490680 is limited relative to the liner 7 according to the present invention, as well as the diameter deviations less acceptable in the case of the known liner compared to the present invention. This improvement is defined by the transition of axis R2 to axis Rl near diameter d3. This improvement over the prior art can be summarized at the point of contact B of the chamber 18 with the coupling sleeve; this allows the liner 7 to be blocked at the end of the thin tube, while facilitating adhesion despite the small diameter, small gap and therefore low inclination of the liner 7 to the Χ-Χ axis.

The inserts 7 increase the slip resistance of the proposed device and prevent it from slipping into the outer portion of the coupling 15 in the event of high pressure fluid flowing through the coupled pipes. The inserts 7 improve the grip of the bearing 2 in the chamber 18. Due to the angle s, the insert 7 head 9 u

the surface practically perpendicular to the Χ-Χ axis and parallel to this surface at level 17 of the coupling support.

In the slope of the axis Χ-/ in the free position / Figures 1 and 4A /, due to the flexible slope or angular displacement, due to the elastic mass of the uncompressed element 1; and, due to its flexible edge 5, the inserts 7 cause a slight resistance to the thin-end inlet, facilitate its axial insertion into the tube TI sleeve 15 / 4A /, as well as its easy axial retraction to the optimum inclination angle of the locking system.

The gripping area of the spikes 11 of the inserts 7 on the end 20 is protected by the external edge of the fluid 5 / Fig. 4B / which completely closes the entrance to the coupling 15.

In connection with the change in the contact contact of the liner 7 with the chamber 18 / Fig. 5-7 / Vol. y. due to the possibility of moving from point C to two points A and B, and due to this conditioned change in the axes R1 and R2 depending on the outer diameter d2, d3 and d4 of the thin tube end T2, the reaction angle x changes to a certain optimum effective clamping of the end 20 is achieved with a large diameter tolerance range between d2 and d4.

By alternating the head support 9 of the head 9 into the chamber 18 / Fig. 5-7 / and thereby theoretically changing the axes R 1 and R 2, the insert 7 acts as a low length and high inclination insert at small ring gaps; poor adhesion of the spike 11 is thereby obtained when, at high annular spacing / j 4 /, the insert 7 acts as a insert of high length and low inclination; this achieves an efficient fixation of the pipe joint.

Finally, the tolerances on the diameters are significantly increased and therefore the entire diameter range of the tube T2 / d2, d3, d4 / is also increased.

If necessary, further increase this range of pipe diameters, i.e. y. tolerances in their diameters shall be replaced by a second series of liners of different lengths than liner 7 and replaced by a single series of liners 7.

Claims (12)

DEFINITION OF INVENTION 1. Anchoring device for hermetically sealing pipe ends - a sleeve / sleeve / end 15 of a first tube T1 and a thin end 20 of a second tube T2 having a massive element 1 and a ring support 2 made of a resilient material, spaced at equal intervals by a circle in said annular abutment 2 according to a cone of a given cone whose axis coincides with the axis X - X of this device such that each insert 7 is directed from this device towards its axis Χ-Χ, except that each of said inserts 7 has a spike. 11 for engagement with the thin end 20 of the second tube T2, which is made to bend at an angle with the support 2 at the moment of connection of the tubes and locking of the thin end 20 within a wide range of tolerances (diameters d2, d3, d4). Device according to claim 1, characterized in that each insert 7 has an element with a rectangular cross-section 8 and has a curved profile. 3. Device according to claim 1, characterized in that each insert 7 has a large head 9 inserted in the annular channel passage 2, an elongated member 10 which cuts at an angle 2 with respect to the axis X-X of this device and forms an obtuse inclination angle (a, ai). with a head 9 as well as a spike 11 extending from the device towards its axis X-X. 4. Device according to claim 1, characterized in that the spike or the head 9 of each insert 7 in the annular support 2 is completely covered by an elastic material. 5. A device according to claim 1, characterized in that it has a radially extending extension of said annular support 2 with respect to said support, which has an inclined edge 5 coincident with the axis X-X of said device, at least up to and including the minimum internal diameter of said massive element 1. the element having an inner annular passageway 4 with respect to which the spike 11 and part of its element 10 extend into the X-X axis. 6. A device according to claim 5, characterized in that the inclined annular rib 5 and each insert 7 have substantially the same inclination to the axis X-X of this device. 7. A device according to claim 5, characterized in that the inner annular passageway 4 has an oblique flange in contact with the element 1 and an oblique flange formed by an annular rib 5 as well as an annular gap 12 formed between the inserts 7 and each of the first flanges. annular gaps 12, and there are annular gaps 13 between the liner and each of the second flanges. An airtight telescopic joint of two collapsible tubes with a locking lock between the two tubes T1 and T2, wherein the first tube T1 with the sleeve end 15 is connected to the sleeve 15 with the second tube T2 having a thin end 20 such that the device according to claim 1 is radially compressed. directionally compressing the massive element 1 radially between the chamber 16 of the first tube T1 and the thin end 20 of the second tube T2, furthermore, the annular support 2 is resting on the annular chamber 18 at the inlet end 15 and each liner 7 and a spike 11 to the thin end 20, characterized in that each insert 7 is inclined with respect to this device and the axis X-X of the two connecting tubes, with a inclination depending on the allowable deviations in the diameter of the thin end 20 (diameters d3, d4) an annular gap (j2, j3, j4) between the thin end 20 and 5 Couplings 15 Ring Inlet Chambers 18. 9. Joining according to claim 8, characterized in that each insert 7 is supported by the head 9 on the inlet sleeve 18 at at least one point (A, B, C, E). 10 and pin 11 coupled to the thin end 20 at any tolerance in diameter for this end and • manufactured with the capability of being displaced to an optimum inclination device in accordance with claim 1 with respect to the X-X axis, and both connecting tubes being rotated 15 around one of the imaginary axes (R1, R2). 10. Joining according to claim 9, characterized in that each insert 7 is supported by the head 9 at two points 18 (A, B) of the inlet sleeve and 20 is connected by a spike 11 to the thin end of the tube T2