IMPROVEMENTS IN PIPE COUPLINGS AND COUPLED PIPE JOINTS

Abstract: A pipe coupling has a body (1) with a sleeve at one end to receive plastic pipe (P). The sleeve has annular saw-tooth profile serrations and a groove housing an O-ring. A radial compression clamp (3) is used to force pipe (P) onto the serrations and in this action considerable movement takes place in the tightening and arrangements are provided to ensure that there is no side-strain or binding on the bolt (6). This is achieved in the following manner; The clamp lugs (7) are laterally machined in the form of a segment of a circle (8). Located in these segments are half round blocks (9) centrally drilled to accept the bolt (6) and free to axially rock in the circular segment (8). The clamp lugs (7) are bored with a clearance hole (10) sufficiently large to provide clear­ ance on the bolt when the lugs have undergone maximum movement due to closing. In the fully tightened position the bolts are correctly longitudinally loaded, and no side-strains or binding arises due to the closing action of the clamp. The bolts are tightened by action on the nuts (11), located one at each end of the bolt.

Description: TITLE Improvements in pipe couplings and coupled pipe #oints. This invention relates to pipe couplings and coupled pipe joints to provide a pipe joint of high mechani-cal strength mainly for use on pipes of plastics or other materials of a similarly deformable or malleable kind. This invention is particularly directed to the provision of a pipe jointing system for pipes having an outside diameter greater than 63 mm, although the invention may equally be used with pipes of smaller diameters. Up to and including pipes of 63 mm diameter or thereabouts, the associated pipe fittings, of the widely used compression type, comprise a body with a prepared socket to accept the pipe end and a metallic or resilient¯ rubber-like sealing ring located in a prepared annular chamfer in the socket mouth. This sealing ring is operatively contacted by a nut coacting with a screw thread on the fitting body and the tightening of the nut closes the sealing ring down circumferentially onto the pipe to provide both a seal and to mechanically grip the pipe. There are many variations on this principle some of which have been developed to a high degree of sophistication. However, the limit of the capability of this type of joint is finally determined by the size of the nut and the associated spanner and effort required to tighten it. This limitation is normally reached at about 65 mm pipe diameter and at sizes above this the nuts become so large that the physical effort required to tighten them becomes unacceptable. On pipe sizes larger than this, the traditional solution is to use fittings operating on a similar principle, with a body having prepared socket and sealing ring, but equipped with a flange and a mating gland having a number of tie bolts or set screws spaced around the periphery and which can be tightened in sequence to drive the gland forward and thus close down the compression ring (see Figure 1). Inevitably fittings of this type are bulky and there are a large number of components involved, in consequence the costs of such fittings become disproportionately high at the point of transition from the largest of the nut types to the smallest of the gland/flange types. If the pipe system is such that corrosion is not of vital importance the flange type fittings can be then manufactured from ferrous materials such as ductile or malleable iron or steel whereby the costs are not prohibitive. However, if corrosion resistance is required and flange type fittings are manufactured from non-ferrous materials such as bronze or gunmetal, then costs rise dramatically and indeed may become unacceptable. One main object of this invention is to produce a joint of the required standard, using less material and components in order that non-corrosive joint systems can be made without costs being prohibitive. The invention is not necessarily confined to non-ferrous materials but could also be equally applied to ferrous materials. According to this invention there is provided a pipe coupling comprising a tubular body with a pipe fitting or coupling at one end, the other end having a sleeve to be received in the bore of a deformable pipe, the sleeve having a series of outer circumferential annular serrations and preferably a groove in the sleeve located in the zone of the serrations and containing a "0" ring to sealingly engage the bore of a pipe, a clamp of annular form to embrace the outer periphery of a pipe, the clamp including lugs disposed each side of a division therein, the lugs receiving a clamp bolt passing therethrough and operative to compress the ends of the clamp at the division to force the pipe onto the serrations and into compressive engagement with the O-ring, the bolt acting through bearing blocks on each lug, each block and a respective lug having complementary coacting arcuate surfaces permitting relative movement about a line extending parallel with the longitudinal axis of the coupling. The serrations preferably are close spaced and of saw-tooth shape, the ramp surface of which lies in the direction of the end of the sleeve. Advantageously the serrations are arranged by their angle and tddth to penetrate sufficient to provide resistance to rated tensile loads of the pipe. The couplings are principally for use on plastic pipes of high quality and controlled specification for use in the conveyance of natural gas and liquid petroleum gas. The same couplings can be used for water supply and similar less stringent applications. The invention is further described and illustrated with reference to the accompanying drawings and by way of an embodiment shown as an example in Figures 2 to 5. In the drawings: Figure 1 shows a longitudinal section through a known prior-art coupling for larger diameter pipes, Figures 2a and 2b show in side view, a pipe coupling according to this invention before and after tightening respectively, Figures 3a and 3b show end views of the coupling shown in Figures 2a and 2b respectively, Figures 4a and 4b show part sections on A-A and# B-B through the coupling of Figures 3a and 3b respectively, and Figure 5 shows a detail of a bearing block. Prior Art Drawing Referring firstly to Figure 1 showing known art this comprises a gland coupling with a body 8, sealing ring S, gland G, a number of bolts or set screws C and an internal liner L to support the polyethylene pipe P. This liner L is essential to provide support for the pipe and resistance to inward collapse under the forces imparted by the compression rings. The actual sealing joint is made on the outside surface of the pipe P. Description of Embodiment of Invention Figures 2, 3 and 4 show a coupling according to the invention. This fitting has no body barrel in the conventional sense and thus eliminates the heaviest and most expensive single item. The liner which is essential to support the pipe is formed to serve the dual purpose of support liner and body. The sealing joint is effected on the inside diameter of the pipe instead of the outside as in known devices. In the drawings the body liner 1 is for purpose of illustration shown as terminating in a male screw thread Ia, but could be a female thread, or a flange to connect up with a mating flange on, for example, a valve, or the body liner could be made double ended for a pipe joint for plastic pipe to plastic pipe to be made at each end as would be the case in a straight coupling. The body of the liner is made to a diameter which will easily slide into the bore of the plastic pipe and is provided with a number of annular serrations 2 (see Figure 4) the purpose of which are to penetrate the inside wall of the plastic pipe to a controlled and limited amount when the pipe is closed downwards under the action of the clamp 3. The penetration of these serrations provide the joint with the mechanical strength required to make the joint stronger than the pipe itself when submitted to a tensile pull to failure point of the pipe. The body liner is further provided with an accurately machined groove 4 (Figure 4) in which is located an nO" ring 5 the purpose of which is to provide a hermetic gas or fluid seal on the inside of the pipe. The clamp 3 is actuated by means of a single low stressed bolt or stud of ample proportions 6. Reference to Figures 2b, 3b and 4b shows the finally tightened position and the relative movement of the lugs from the untightened position shown in Figures 2a, 3a and 4a. Considerable movement takes place in the tightening and arrangements are provided to ensure that there is no side-strain or binding on the bolt. This is achieved in the following manner: The clamp lugs 7 are laterally machined in the form of a segment of a circle 8. Located in these segments are half round blocks 9 (see Figure 5) centrally drilled to accept the bolt 6 and free to axially rock in the circular segment 8. The clamp lugs 7 are bored with a clearance hole 10 sufficiently large to provide clearance on the bolt when the lugs have undergone maximum movement due to closing, and as illustrated in Figure 2b. It will be seen from Figure 3b that in the fully tightened position the bolts are correctly longitudinally loaded, and that no sidestrains or binding arises due to the closing action of the clamp. The bolts are tightened by action on the nuts 11, located one at each end of the bolt. With a conventional fitting using a nut or glands with bolts, the forces applied are parallel to the axis of the pipe, and the radially closing down effect is only achieved by the diversion of sealing rings or similar down an inclined surface of an annular bevel, i.e. only a part of the applied effort is available for closing down. On the clamp of this invention the bolt is working at right angles to the pipe axis and thus practically the whole of the effort applied is available to force the pipe downwards to overcome the wide ¯tolerance possibility and also to sink the inside of the tube into the serrations. In this way only one bolt is required instead of the 4 or more on a conventional design. The number and depth of serrations is important as the serrations have the effect of creating a multiple shear resistance to the pull of the pipe under tension. If the shape of the serrations allows too much penetration into the pipe, then the pipe would be weakened and fail within the joint. If there were too few serrations then there would be an insufficient multiple shear resistance and the pipe would pull out before pipe failure occurred. (4+ tonnes resistance required at 90 mm size). If there were too many serrations then insufficient penetration occurs, this is because the total effort applied by the clamp is finally resisted by the number of serrations. Because the clamp is more effective in closing force than the conventional types, then the serrations can be grouped in a much smaller space. In this way the body liner is much shorter than the liner on a conventional fitting with consequent savings in materials and costs. Possibly the blocks 9 and lugs 10 could have other shape coacting surfaces such as spherical.

Claims: CLAIMS 1. A pipe coupling comprising a tubular body with a pipe fitting or coupling at one end, the other end having a sleeve to be received in the bore of a deformable pipe, the sleeve having a series of outer circumferential annular serrations, a clamp of annular form to embrace the outer periphery of the pipe, the clamp including lugs disposed each side of a division therein, the lugs receiving a clamp bolt passing therethrough and operative to compress the ends of the clamp at the division to force the pipe onto the serrations, the bolt acting through bearing blocks on each lug, each block and a respective lug having complementary coacting arcuate surfaces permitting relative movement about a line extending parallel with the longitudinal axis of the coupling. 2. A pipe coupling in accordance with Claim 1, wherein an annular groove is provided in the outer periphery of the sleeve in the zone of the serrations, the groove containing an 'O" ring to sealingly engage the bore of the pipe, when the pipe is brought into compressive engagement therewith. 3. A pipe coupling in accordance with Claim 1 or 2, wherein the coacting surfaces of a block and a lug are cylindrical. 4. A pipe coupling in accordance with any preceding claim, wherein the bolt has threaded ends each engaging a nut bearing against a surface of a block. 5. A pipe coupling in accordance with any preceding claim, wherein the serrations are close spaced and of saw-tooth shape, the ramp surface of which lies in the direction of the sleeve. 6. A pipe coupling in accordance with any preceding claim, wherein a groove containing an "O" ring is positioned between two zones of serrations. 7. A pipe coupling in accordance with any preceding claim, wherein the bearing blocks are of part cylindrical shape, the bolt acting on planar surfaces of the block. 8. A pipe coupling in accordance with any preceding claim, uherein the lugs have bores to receive the clamp bolt, the bores being of a diameter to allow free clearance of the bolt in both the uncompressed and compressed positions.

Inventors: LARGE, JACK ADRIAN
Applicants: KAY & COMPANY (ENGINEERS) LIMITED
Application year: 1983
Main classification: F16L47
IPC codes: F16L47