Improvements in and relating to pipe joints

Abstract: The invention provides a pipe joint comprising first and second outer pipe members (1,2); means (3,4) for connecting first and second outer pipe members (1,2) in an end-to-end fashion so as to provide a fluid-tight seal therebetween, the fluid-tight seal being capable of withstanding internal pressures of at least 1000 psi; and, arranged within at least the first outer pipe member (1), a first inner liner pipe member (6) formed of a polymeric material; the liner pipe member (6) being provided at its end with a radially outwardly extending stub flange (8); an annular supporting hoop (12) being disposed in an annular groove (10) in the end face of the stub flange (8); the first and second outer pipe members (1,2) together defining on their respective radially inner surfaces an annular recess (5) for retaining the stub flange (8) of the liner pipe member (6) and for clamping the stub flange (8) in place to hold it against axial displacement.

Description: This invention relates to improved pipe joints and in particular pipe joints of the type suitable for high pressure pipelines such as the pipelines used in off-shore applications. Off-shore pipelines, such as those used to pump oil and gas ashore from off-shore drilling rigs and terminals, typically are constructed so as to be capable of withstanding very high internal pressures. For example, it is rare for the maximum pressures generated within a given pipeline to be less than 13.79 x 10 6 N/m 2 (2000 psi) and frequently pressures are significantly higher. This contrasts with the internal pressures generated within pipelines used for domestic utilities such as domestic gas and water where the internal pressures rarely exceed more than about 1.38 x 10 6 N/m 2 to 2.07 x 10 6 N/m 2 (200 to 300 psi). The high pressures encountered in off-shore pipelines arise in part because of the high well pressures encountered with gas and oil wells, and in part by the fact that it is necessary to pump the contents of the pipeline over long distances using only a single pumping station and consequently high pump pressures are required. The pipelines used in such off-shore situations need to be strong and durable and therefore typically are formed from steel. Lengths of steel pipe are joined by means of welding and/or couplings of a mechanical nature which are typically of the "pin and box" type. In "pin and box" couplings, the box is constituted by a socket formation which may have a parallel walled or flared inner bore, and the pin is shaped so as to fit into and be retained in the socket. The mating surfaces of the "pin" and "box" may be threaded, or may have a snap-fit construction, by way of example. Metal-to-metal seals formed between the pin and box are capable of withstanding pressures of many thousands of pounds per square inch. Metal-to-metal connections of this type are well known and have been the subject of extensive research and development. One problem encountered with metal pipe lines in general, and off-shore pipelines in particular, is the problem of corrosion. It is undesirable from an economic standpoint to construct pipelines of stainless steel, and therefore the somewhat cheaper carbon steels are often used for the construction of the pipes. It is therefore necessary to include an allowance in the wall thickness for corrosion or to protect the pipes against corrosion in some way and, for example, the outer surface of the pipe may be protected by means of an appropriate surface treatment or covering. In order to protect the inner bore of the pipe from corrosive effects of materials passing through the pipe, it is possible to provide a liner formed of a polymeric material such as a polyolefin. A further problem encountered with such pipelines is to ensure that the joints between adjacent lengths of liner pipe can withstand the high internal pressures and tensile stresses encountered in use. Where mechanical joints are employed for the liner pipes, it can be difficult to ensure the integrity of the joint over a prolonged period. This is because the liner pipes may be subject to periodic tensile stresses of considerable magnitude. Such stresses are the result of a number of factors such as flow induced vibration, the swelling of the pipeline materials due to the nature of the products passing through the pipelines, and thermal expansion and contraction. Moreover, the methods for installing the liner pipes, which generally involve hauling the liner through the pipe, tend to set up tensile stresses in the pipe from the outset. The resultant effects of these various periodic tensile stresses on the liner pipe is that one liner pipe member can be pulled away from its joint with an adjacent pipe liner member and displaced axially along the pipeline. Various attempts have been made to overcome this problem but at the present time there remains a need for a pipe joint of the aforesaid type which can provide a means of firmly anchoring the liner pipe members in place so as to prevent loss of liner pipe joint integrity and consequent leakage of the contents of the liner pipe into the annular space between the liner pipe and steel outer pipe. Existing known mechanical anchorages or joints for liner pipes rely on a gripping action, the effectiveness of which will reduce with time and lining temperature fluctuations. EP-A-0 441 619 discloses a pipe joint between two stub-flanged plastics pipes in which the stub flanges of the pipes are provided with reinforcing hoops. However, there is no disclosure or suggestion in this document of a means of overcoming the abovementioned problems encountered with offshore pipelines. US-A-3 650 550 discloses the use of a perforated reinforcing hoop for strengthening the flange of a liner pipe against cold flow. Again, however, this document does not address the aforementioned problems encountered in off-shore pipelines. In a first aspect, the invention provides a pipe joint comprising first and second outer pipe members; means for connecting the first and second outer pipe members in an end-to-end fashion so as to provide a fluid-tight seal therebetween, the fluid-tight seal being capable of withstanding internal pressures of at least 6.895 x 10 6 N/m 2 (1000 psi); and, arranged within at least the first outer pipe member, a first inner liner pipe member formed of a polymeric material; the liner pipe member being provided at its end with a radially outwardly extending annular stub flange; an annular supporting hoop being disposed in an annular groove in the end face of the stub flange; the first and second outer pipe members together defining on their respective radially inner surfaces an annular recess for retaining the stub flange of the liner pipe member and for clamping the stub flange in place to hold it against axial displacement, wherein the annular recess comprises a pair of generally radially extending confronting surfaces and a generally axially extending surface linking the said generally radially extending surfaces. The term "pipe members" as used herein refers not only to pipes as such but also to pipe couplings, pipe connectors and pipe fittings such as T-pieces, bends, adaptcrs, valve housings etcetera. The first and second outer pipe members are generally formed of a suitable metal such as an appropriate grade of carbon steel. The joint between the outer pipe members is typically constructed so as to be capable of withstanding internal pressures of 34.47 x 10 6 N/m 2 (5000 psi) or more. The means for connecting the first and second outer pipe members may take the form of a thread on a radially outer surface of one of the outer pipe members which engages a thread on a radially inner surface of the other outer pipe member. However, as one alternative the first and second outer pipe members may be provided with annular ridges, recesses or other formations which enable the pipe members to be coupled together in a snap-fit joint. As another alternative, the first and second outer pipe members may be provided with flanges or other like constructions which enable the pipe members to be secured together by external securing means such as flange bolts and clamping arrangements. In one embodiment, both the first and second outer pipe members are pipes, the second outer pipe member having an inner liner pipe member as hereinbefore defined arranged therein. Accordingly, the invention also provides a pipe joint comprising first and second outer pipe members; means for connecting the first and second outer pipe members in an end-tc-end fashion so as to provide a fluid-tight seal therebetween, the fluid tight-seal being capable of withstanding internal pressures of at least 6.895 x 10 6 N/m 2 (1000 psi); and, arranged within the outer pipe members, first and second inner liner pipe members formed of a polymeric material; the liner pipe members being provided at their facing ends with radially outwardly extending annular stub flanges providing mating surfaces between the two liner pipes generally normal to the axial direction of the liner pipes; an annular supporting hoop or hoops being disposed in an annular groove in the mating faces of each stub flange; the first and second outer pipe members together defining on their respective radially inner surfaces an annular recess for retaining the stub flange of the liner pipe members and for clamping the stub flanges together to form a fluid-tight seal therebetween, wherein the annular recess comprises a pair of generally radially extending confronting surfaces and a generally axially extending surface linking the said generally radially extending surfaces. The inner liner pipe member or members is or are formed from a suitable polymeric material, and examples of such materials include polyolefin homopolymers and co-polymers thereof. Examples of polyolefins suitable for use in constructing the liner pipes include polypropylene and polyethylene, for example HDPE, LDPE, MDPE, etc. Other materials which may be used as alternatives to polyolefins include polyvinylidene difluoride (PVDF). The liner pipe members may have single layer or multilayer pipe walls. For example, the liner pipe members may have one or more barrier layers formed from a barrier material such as a polyamide, in addition to a polyolefin layer. The barrier layer serves to prevent or reduce permeation of hydrocarbons through the liner wall. The abutting ends of the liner pipe elements have stub flanges, the term "stub flanges" being a term well known in the art. The stub flanges are compressed together by the walls of the annular recess on the inner OD of the outer pipe members as the outer pipe members are tightened against each other, such that a seal is formed between the abutting stub flanges. The stub flanges preferably have an initial axial dimension greater that the axial length of the annular recess in order to increase the degree of compression of the stub flanges as the outer pipes are tightened together. The stub flanges are each provided with an annular recess in their end faces in which are located reinforcing hoops usually formed of a metal material such as steel. The reinforcing hoops of the respective stub flanges act as reinfcrcing struts and serve to strengthen the stub flange and serve to prevent it from being displaced from the joint by the periodic tensile stresses encountered by the liner pipe members in use. The annular recess defined by the outer metal pipe members will be disposed at or near the interface between the outer pipe elements. As indicated above, the annular recess comprises a pair of generally radially extending confronting surfaces and a generally axially extending surface linking the said generally radially extending surfaces. The arrangement will usually be such that one radially extending surface is provided by one pipe element and the other radially extending surface is provided by the other pipe element. The generally axially extending surface may be provided by one of the pipe elements, or by both. In one embodiment, the stub flange of the or each inner liner pipe element may be formed of a cross-linked material so as to strengthen the stub and render it more elastic. This would have the effect of increasing its resistance to being pulled out of the joint through axial end loads. Moreover, the elasticity imparted by crosslinking should assist in reducing or eliminating compressive stress relaxation, a problem which could otherwise lead to the integrity of the seal between the flanges being reduced after a period of time in service. In order to increase the ability of the stub flanges to resist axial movement of the liner pipe, and also to enhance the seal between the ends of the polymeric liner pipe members, the respective stub flanges of the liner pipe members may be welded together during installation. In one embodiment, the respective stub flanges may be friction welded together. Thus, when a screw-threaded connection is provided between the outer metal pipe , the friction between the stub flanges caused by one stub flange being rotated relative to the other as the outer pipe members are screwed together may generate sufficient heat to cause fusion of the polymeric material at the surfaces of the stub flanges. As an alternative, or in addition to any friction-welding of the stub ends of the liner pipe members, a heat induction coil may be inserted along the string of pipes being assembled, the coil being used to energize and heat the reinforcing hoop at the stub interface to cause the polymeric material of the stub flanges to fuse and weld together. In a further embodiment, the invention provides a process for forming a pipe joint of the aforesaid type in which the hoop reinforced stub flange is formed in situ using a hot forming technique. For example, an induction heated sleeve may be placed about the end of a plain ended polymeric pipe member to soften or melt the said end, and a jacking head having a reinforcing hoop supported thereon urged against the softened or melted end so as to deform it radially outwardly into the shape of a stub flange, the reinforcing hoop being embedded in the stub flange as it is formed. One of several advantages of forming the stub flange in situ in this way is that the process would create hoop retaining lips which would assist in holding the reinforcing hoop in place. The invention will now be illustrated by reference to the particular embodiments shown in the accompanying drawings of which: Figure 1 is a longitudinal partial sectional elevation through a pipe joint according to one embodiment of the invention; Figure 2 is an enlarged view of the part of the sectional elevation of Figure 1; Figure 3 is an enlarged partial sectional elevation of a second embodiment of the invention; Figure 4 is an enlarged partial sectional elevation of a third embodiment of the invention; Figure 5 is a partial longitudinal sectional elevation of a fourth embodiment of the invention; Figure 6 is a partial longitudinal sectional elevation of a fifth embodiment of the invention; Figure 7 is a longitudinal sectional elevation illustrating schematically apparatus for forming a stub flange in situ; Figures 8a to 8d illustrate schematically the formation of a stub flange in situ; and Figure 9 illustrates schematically apparatus for softening the end of a plain pipe end prior to stub flange formation. Referring now to Figure 1 it can be seen that a pipe joint according to one embodiment of the invention comprises a pair of steel outer pipe members 1 and 2 connected together, pipe member 1 functioning as a socket or "box" and pipe member 2 functioning as a spigot or "pin". Pipe member or "box" 1 has a flared internal surface 3 which is threaded to engage a mating thread on tapering surface 4 of the "pin" member 2. At radially inner and radially outer locations, the pipe members 1, 2 have axially facing wall portions 1a, 1b, 2a, 2b which are forced into sealing contact as the "pin" member 2 is screwed into the "box" member 1. The metal-to-metal seals formed at 1a, 2a and 1b, 2b are capable of withstanding pressures in excess of 6.895 x 10 6 N/m 2 (1000 psi), and more usually in excess of 34.47 x 10 6 N/m 2 (5000 psi). In order to enhance the sealing capacity of the joint, sealing compounds may be inserted between threaded surfaces 3, 4. Such sealing compounds are well known and their composition need not be discussed here. Arranged radially inwardly of the steel pipe members 1 and 2 are liner pipe members 6 and 7 formed from a polymeric material such as polyethylene. Liner pipe members 6, 7 each have stub flanges 8, 9 which are accommodated in an annular recess 5 extending around the inner diameter of the steel pipes 1 and 2 in the region of the junction therebetween. The formation of the annular recess 5 is illustrated in more detail in Figures 2, 3 and 4. The stub ends of the polymeric liner pipe elements 6, 7 each have annular recesses 10, 11 in their end faces. Located within each recess 10, 11 are reinforcing hoops 12, 13 formed from a steel material. It will be appreciated that rather than each stub end being provided with its own reinforcing hoop, a single reinforcing hoop of the appropriate axial thickness could be employed. In this embodiment, the stub flanges 8, 9 of the polymeric liner pipes 6, 7 are formed from non-crosslinked polyethylene but they could advantageously be crosslinked prior to service for example by irradiation from a suitable source such as a cobalt 60 source. Typically, irradiation would be carried such that the absorbed doses of ionising radiation fall within the range 0-300 kiloGray, preferably 50-250 kiloGray, and more preferably 150-200 kiloGray. The formation of the annular recess 5 is illustrated in more detail in Figures 2, 3 and 4. In Figure 2, there is shown an arrangement wherein each of the steel pipe elements, 1 and 2 is provided at a radially inner location on its end face with annular recesses 21, 22. The annular recess of pipe element 1 is defined by a radial end wall 21a and an axially extending wall 21b. Similarly the annular recess of pipe element 2 is defined by radially extending wall 22a and axially extending wall 22b. Disposed radially outwardly of the recess 5 are abutting end walls 1b and 2b as described above. In this embodiment, the recess 5 spans the junction between the two pipe elements 1 and 2. In Figures 3 and 4, the recess 5 is offset slightly from the junction between the pipe elements 1 and 2. In Figure 3, the recess is defined by radially extending wall 31a and axially extending wall 31b of the "box" pipe element 1 and radially extending wall 32a of the "pin" pipe element 2. In Figure 4, the converse arrangement exists, with the recess 5 being defined by radially extending end wall 42a and axially extending wall 42b of the "pin" element 2 and the radially extending wall 41a of the "box" pipe element 1. In use, the liner pipes 6, 7 are arranged within their associated metal pipe members 1, 2 and the pipe members 1, 2 are screwed together using methods known per se. As the pipe elements 1, 2 are screwed together so the stub flanges 8, 9 are compressed against each other to form a seal. Moreover, since one of the stub flanges will be rotating relative to the other as the pipe elements 1, 2 are tightened together, the resulting friction between the surfaces of the flanges 8, 9 may, depending upon the torque applied to the joint, and the extent of compression of the flanges, lead to sufficient heat being produced to melt or soften the surfaces of the flanges to fuse them together. In this way, a very strong seal is provided between the flanges 8, 9. The reinforcing hoop 12, 13 acts as a strut and prevents the flanges 8, 9 from being deformed radially inwardly and pulled out of recess 5 in response to the periodic high tensile stresses to which the pipe liners are subjected, for example as a result of flow induced vibration, thermal contraction and expansion, or the swelling of the pipe walls that can tend to occur when certain materials are transported through the pipes. In order to provide a still stronger joint, an induction heating coil mounted on a suitable pipeline pig may be manoeuvred into position within the liner pipe members 6, 7 at the region of the interface and the steel reinforcing hoop 12, 13 induction-heated to bring about melting and fusion of the surfaces of flanges 8, 9, if this has not previously taken place through friction heating. Pipe joints of the type shown in Figure 3 have been constructed and tested. Thus, a pair of outer steel pipes of 168.275mm (6⅝") outer diameter (O.D.) and 19.05mm (¾") thick walls incorporating a standard screw integral zero upset connector were provided with an annular recess at the radially inner surface of the joint interface, the annular recess having an axial length of 15.6 = 0.4mm and a radial dimension of 40 ± 0.5mm. Polyethylene liner pipes having an OD of 129.2 ± 0.2mm, a 5mm nominal all thickness and stub flange with a shoulder height of 3.5mm, a shoulder thickness of 8.0mm and a reinforcing hoop of 121.0 ± 0.1mm inner diameter, 4.0 ± 0.2mm radial thickness and 2.0 ± 0.1mm axial thickness, were inserted into the outer steel pipes as shown in the Figure, and subjected to hydrostatic pressure following by tensile loading. The tests showed that no leakage occurred at at east 10.34 x 10 6 Nm -2 (1500 psi) (at which point the test was discontinued) and that disengagement of the stub flange did not occur until the polyethylene liner had been axially loaded to an least 3 Tonnes. The pipe joints of the invention do not necessarily need to be of the "pin and box" type, and alternative forms of construction are shown in Figures 5 and 6. In each of Figures 5 and 6, the radially outer metal pipe elements 51, 52 and 61, 62 are provided with flanges 51a, 52a, 61a, 62a, having abutting end faces 51b, 52b, 61b, 62b, which are generally normal to the axial direction of the pipeline. The flanges 51a, 52a, 61a, 62a are connected together by conventional flange connection means, not shown. Thus with the embodiments illustrated in Figures 1 to 4, the radially outer metal pipe members of Figures 5 and 6 have associated inner liner pipe members 53, 54 and 63, 64 formed of a suitable polymeric material such as polyethylene. The liner pipe members have stub flanges 53a, 54a, 63a, 64a, each of which is provided with an embedded steel reinforcing hoop 55, 56, 65, 66, the purpose of which is the same as the reinforcing hoop described in respect of Figures 1 to 4 above. As with Figures 1 to 4, the radially inner surfaces of the outer metal pipe members 51, 52, 61, 62 together define an annular recess 57, 67 into which the stub ends of the liner pipes fit. As can be seen, the annular recess can span the junction between the two radially outer metal pipes, as shown in Figure 5, or can be offset relative to the pipe junction, as shown in Figure 6. The outer pipe members can be pipes as such, or they can be any one of a number of pipe couplings and connectors. As will be appreciated, a pipe may be formed with integral "pin" and "box" configurations, or it may be formed with two "pin" ends, a separate double "box"-ended connector being used to connect adjacent lengths of pipe. Similarly, in principle at least, a pipe can be provided with integral twin "box" ends which would connect to a "pin"-ended connector. Furthermore, "pin" or "box" adaptors can be welded to the ends of plain ended pipes. It will be appreciated that the various permutations are numerous and the foregoing are given merely by way of example. The installation of the liner pipe elements within the outer steel pipe can be made easier by inserting the liner pipe elements as plain ended pipe elements and then forming the stub flanges in situ. The formation of the stub flanges in situ is illustrated in Figures 7 to 9. Figure 7 shows an arrangement in which an outer steel pipe member 71 has disposed therein a liner pipe member 72 formed from a suitable polymeric material such as polyethylene. Liner pipe member 72 is plain-ended. The outer steel pipe member 71 has an annular recess 73 running around the radially inner surface of its end face. The apparatus for forming the plain end 72a of the liner pipe member 72 into a stub flange comprises a mandrel or former 74 having an expandable end 75 which has an initial outer diameter corresponding approximately to the inner diameter of the liner pipe element 72. Arranged slidably on the mandrel 74 is a jacking head 76 which is provided with an array of supporting pins 77 for mounting thereon a metal reinforcing hoop 78. Prior to bringing the jacking head and reinforcing hoop into contact with the plain end 72a of the liner pipe member 72, an induction heated sleeve 91, as shown in Figure 9, is first slipped over the end 72a. The induction heated sleeve is used to heat the liner pipe member 72 to a temperature at which it is sufficiently soft to be deformed. The sleeve is then removed, the expandable end 75 of the former 74 is expanded to grip the liner 72 to the outer steel pipe member 71, and the jacking head moved along the outer surface of the mandrel such that the reinforcing hoop 78 is urged into contact with the end 72a of the liner pipe member. By applying suitable force to the jacking head, the reinforcing hoop 78 deforms the softened end 72a of the liner pipe member radially outwardly and into the annular recess 73 of the outer metal pipe member. The various stages in the development of the stub flange are shown schematically in Figures 8a to 8d. In order to assist the deforming process, by keeping the polymeric material of the end 72a of the pipe member 72 sufficiently soft, the reinforcing hoop 78 may be heated, for example by induction heating, or may be ultrasonically activated during the flange forming cycle. By means of this process, the reinforcing hoop 78 also becomes embedded in the newly formed stub flange. The jacking head is then removed along with the mandrel 74 and the stub flange is trimmed to remove any bulges or flashing produced during the moulding process. It will readily be appreciated that numerous modifications and alterations may be made to the pipe joints illustrated in the accompanying drawings without departing from the scope of the claims. For example, although the drawings illustrate a connection between the stub flanges of two liner elements, the joints of the invention are equally applicable to connections in which the annular recess is of a size to accommodate only a single stub flange. Such an arrangement could be employed when joining a length of pipe to a fitting such as a valve or pump. Moreover, the drawings illustrate arrangements in which each stub flange has its own reinforcing hoop. As an alternative, however, a single reinforcing hoop of double thickness could be used to replace the two individual reinforcing hoops. The nature of the metal-to-metal joints between the outer pipe members may also be varied. For example, the "pin" or spigot may have a generally uniform diameter, rather than tapering as shown in the drawings, and the "box" or socket would be shaped accordingly.

Claims: A pipe joint comprising first and second outer pipe members (1, 2); means (3, 4) for connecting the first and second outer pipe members (1, 2) in an end-to-end fashion so as to provide a fluid-tight seal therebetween, the fluid-tight seal being capable of withstanding internal pressures of an least 6.895 x 10 6 N/m 2 (1000 psi); and, arranged within at least the first outer pipe member (1), a first inner liner pipe member (6) formed of a polymeric material; the liner pipe member (6) being provided at its end with a radially outwardly extending annular stub flange (8) ; an annular supporting hoop (12) being disposed in an annular groove (10) in the end face of the stub flange (8); the first and second outer pipe members (1, 2) together defining on their respective radially inner surfaces an annular recess (5) for retaining the stub flange of the liner pipe member and for clamping the stub flange (8) in place to hold it against axial displacement, wherein the annular recess (5) comprises a pair of generally radially extending conforming surfaces (21a, 22a) and a generally axially extending surface (21b, 22b) linking the said generally radially extending surfaces (21a, 22a). A pipe joint according to Claim 1 wherein the fluid tight seal between the first and second outer pipe members (1, 2) is capable withstanding internal pressures of 34.47 x 10 6 N/m 2 (5000 psi) or more. A pipe joint according to Claim 1 or Claim 2 wherein the means (3, 4) for connecting the first and second outer pipe members takes the form of a thread on a radially outer surface of one of the outer pipe members (4) which engages a thread on a radially inner surface of the other outer pipe member (3). A pipe joint according to Claim 1 or Claim 2 wherein the first and second outer pipe members (1, 2) are provided with annular ridges, recesses or other formations which enable the pipe members to be coupled together in a snap-fit joint, or are provided with flanges or other like constructions which enable the pipe members to be secured together by external securing means. A pipe joint according to any one of the preceding Claims wherein the first and second outer pipe members (1, 2) are pipes, the second outer pipe member (2) having an inner liner pipe member (7) arranged therein. A pipe joint comprising first and second outer pipe members (1, 2); means for connecting the first and second outer pipe members (1, 2) in an end-to-end fashion so as to provide a fluid-tight seal therebetween, the fluid tight-seal being capable of withstanding internal pressures of at least 6,895 x 106 N/m2 (1000 psi); and, arranged within the outer pipe members (1, 2), first and second inner liner pipe members (6, 7) formed of a polymeric material; the liner pipe members (6, 7) being provided at their facing ends with radially outwardly extending annular stub flanges (8, 9) providing mating surfaces between the two liner pipes (6, 7) generally normal to the axial direction of the liner pipes; an annular supporting hoop or hoops (12, 13) being disposed in an annular groove (10, 11) in the mating faces of each stub flange (8, 9); the first and second outer pipe members (1, 2) together defining on their respective radially inner surfaces an annular recess (5) for retaining the stub flange (8, 9) of the liner pipe members (6, 7) and for clamping the stub flanges (8, 9) together to form a fluid-tight seal therebetween, wherein the annular recess (5) comprises a pair of generally radially extending confronting surfaces (21a, 22a) and a generally axially extending surface (21b, 22b) linking the said generally radially extending surfaces (21a, 22a). A pipe joint according to any one of the preceding Claims wherein the or each inner liner pipe member (6, 7) is formed from a polymeric material selected from polyolefin homopolymers and co-polymers thereof, or polyvinylidene difluoride. A pipe joint according to Claim 7 wherein the or each inner liner pipe member (6, 7) is formed from polypropylene or polyethylene. A pipe joint according to any one of the preceding Claims wherein the or each inner liner pipe member (6, 7) has a single layer pipe wall. A pipe joint according to any one of Claims 1 to 8 wherein the or each inner liner pipe member (6, 7) has a multi-layer pipe wall. A pipe joint according to Claim 10 wherein the or each liner pipe member (6, 7) has one or more barrier layers formed from a barrier material which prevents or reduces permeation of hydrocarbons through the liner pipe wall. A pipe joint according to Claim 11 wherein one radially extending surface (21a) is provided by one outer pipe member (1) and the other radially extending surface (22a) is provided by the other outer pipe member (2). A pipe joint according to Claim 11 or Claim 12 wherein the generally axially extending surface is provided by one of the pipe members (1). A pipe joint according to Claim 11 or Claim 12 wherein the generally axially extending surface is provided by both of the pipe members (1, 2). A pipe joint according to any one of the preceding Claims wherein the stub flange (8, 9) of the or each inner liner pipe member (6, 7) is formed from a crosslinked material. A pipe joint according to Claim 6 or any Claim dependent thereon wherein the respective stub flanges (8, 9) of the inner liner pipe members (6, 7) are welded together. A pipe joint according to Claim 16 wherein the respective stub flanges (8, 9) are friction welded together. A pipe joint according to Claim 16 wherein the respective stub flanges (6, 9) have been welded together by induction heating. A process for forming a pipe joint wherein a hoop reinforced stub flange (8, 9) as defined in any one of the preceding claims is formed in situ using a hot forming technique. A process according to claim 19 wherein for example, an induction heated sleeve is placed about the end of a plain ended polymeric pipe member to soften or melt the said end, and a jacking head having a reinforcing hoop supported thereon urged against the softened or melted end so as to deform it radially outwardly into the shape of a stub flange, the reinforcing hoop (12, 13) being embedded in the stub flange as it is formed.

Inventors: HEADFORD ALAN LLOYD, HEADFORD, ALAN LLOYD
Applicants: VICTAULIC PLC
Application year: 1996
Main classification: F16L23
IPC codes: B29C57, B29C35, B29B13, F16L58, B29C70, F16L23, F16L47, B29C43