Patent Description:
Existing pipe joints between pipes in a pressurized pipeline, such as welded lap pipe joints, can be prone to bending or buckling at the pipe joint during geohazard or seismic events, such as at the bell of a first pipe that receives the spigot of a second pipe. The material at the welded connection of the bell of the first pipe to the spigot of the second pipe can be more prone to fracture, such as by hardening of the material during welding. This can increase the risk of failure and the loss of pressure containment during seismic and/or geohazard events, in which the pipes can be subjected to severe axial and/or bending loads. For instance, <CIT> discloses an UOE steel tube and a structure. Moreover, <CIT> describes an air conditioner system. Accordingly, there exists a need for improvements to pipes and pipe joints for pipelines.

Certain embodiments of the disclosure pertain to pipes and pipe joint arrangements, wherein the pipes include deformations, protrusions, or projections formed in the pipes and configured to induce buckling of the pipes at the location of the deformations when subjected to severe loading conditions. According to the present invention, a pipe joint arrangement comprises a first pipe comprising a main body having a first diameter, an end portion and a first pipe wall thickness, and a second pipe comprising an end portion. The end portion of the first pipe is welded to the end portion of the second pipe to form a pipe joint and to seal the pipe joint between the first pipe and the second pipe. The first pipe comprises an outwardly-extending, buckle-inducing deformation that is spaced apart from the pipe joint in an upstream direction, and a crest height of the buckle-inducing deformation is <NUM>% to <NUM>% of the first pipe wall thickness, wherein a contour of the buckle-inducing deformation is symmetric about a longitudinal axis of the first pipe, convex or sine-shaped, and curved from a crest of the buckle-inducing deformation to a regular exterior surface of the main body of the first pipe having the first diameter, and wherein the buckle-inducing deformation is configured to ensure that buckling occur at the preselected location of the buckle-inducing deformation of the first pipe when the pipe joint arrangement is subjected to a geohazard event.

In any or all of the disclosed embodiments, the buckle-inducing deformation comprises an annular bulge formed in an exterior surface of the first pipe and an annular recess formed in an interior surface of the first pipe at the location of the annular bulge.

In any or all of the disclosed embodiments, the first pipe has the longitudinal axis and the buckle-inducing deformation is symmetric about the longitudinal axis.

In any or all of the disclosed embodiments, the first pipe has the longitudinal axis, and the buckle-inducing deformation is axially spaced from the pipe joint by <NUM> (<NUM> inches) to <NUM> (<NUM> inches) along the first pipe.

In any or all of the disclosed embodiments, the buckle-inducing deformation is axially spaced from the pipe joint by <NUM> (<NUM> inches) to <NUM> (<NUM> inches) along the first pipe.

In any or all of the disclosed embodiments, the crest height of the buckle-inducing deformation is from <NUM>% to <NUM>% of the first pipe wall thickness.

In any or all of the disclosed embodiments, the end portion of the first pipe is configured as a pipe spigot, the second pipe comprises a main body having the first diameter, and the end portion of the second pipe is configured as a pipe bell comprising a second diameter greater than the first diameter. The pipe spigot is inserted into the pipe bell and welded to the pipe bell.

In any or all of the disclosed embodiments, the crest height is from <NUM>% to <NUM>% of the first pipe wall thickness.

In any or all of the disclosed embodiments, the first pipe wall thickness is <NUM> (<NUM> inch) and the crest height is <NUM>% to <NUM>% of the first pipe wall thickness, or the first pipe wall thickness is <NUM> (<NUM> inch) and the crest height is <NUM>% to <NUM>% of the first pipe wall thickness.

In any or all of the disclosed embodiments, the crest of the buckle-inducing deformation does not extend beyond a height of an exterior surface of the second pipe.

In any or all of the disclosed embodiments, the pipe joint is a butt-welded pipe joint.

In any or all of the disclosed embodiments, the butt-welded pipe joint further comprises a reinforcing member disposed around the end portion of the first pipe and around the end portion of the second pipe, the reinforcing member being welded to the first pipe and to the second pipe. The second pipe comprises a buckle-inducing deformation formed in the end portion of the second pipe on the opposite side of the butt-welded pipe joint from the buckle-inducing deformation of the first pipe.

In any or all of the disclosed embodiments, the buckle-inducing deformation of the first pipe is one of a plurality of buckle-inducing deformations formed in the first pipe and spaced apart from each other along the longitudinal axis of the first pipe.

According to the present invention, a method comprises welding the first pipe to the second pipe to form the pipe joint arrangement of any of the disclosed embodiments.

In any or all of the disclosed embodiments, the buckle-inducing deformation is formed by positioning the first pipe over a plurality of dies of an expander apparatus, the first pipe being at ambient temperature, and each of the plurality of dies comprising a flange and a curved rod member coupled to a radially outward surface of the flange. The dies are moved radially outwardly from a central axis of the expander apparatus such that the rod members of the dies are pressed into an interior surface of the first pipe to form the buckle-inducing deformation in the first pipe.

In any or all of the disclosed embodiments, the buckle-inducing deformation is formed by positioning the first pipe between a first die and a second die of a grooving machine, the first pipe being at ambient temperature, the first die comprising a groove and the second die comprising a forming member. The first pipe is pressed between the first die and the second die, and the first pipe is rotated such that the forming member forms the buckle-inducing deformation in the first pipe.

According to the present invention, a pipeline comprises the pipe joint arrangement of the present invention.

In any or all of the disclosed embodiments, the buckle-inducing deformation is spaced from an end of the first pipe by <NUM> (<NUM> inches) to <NUM> (<NUM> inches) along the first pipe.

In any or all of the disclosed embodiments, the end portion of the first pipe is configured as a pipe spigot, the second pipe comprises a main body having the first diameter, and the end portion of the second pipe is configured as a pipe bell comprising a second diameter greater than the first diameter. The buckle-inducing deformation is spaced apart from the pipe spigot such that when the pipe spigot of the first pipe is received in the pipe bell of the second pipe, the buckle-inducing deformation is offset from the pipe bell of the second pipe.

In any or all of the disclosed embodiments, a crest height of the buckle-inducing deformation is from <NUM>% to <NUM>% of the first pipe wall thickness.

In any or all of the disclosed embodiments, the first pipe wall thickness is <NUM> (<NUM> inch) and the crest height of the buckle-inducing deformation is <NUM>% to <NUM>% of the first pipe wall thickness, or the first pipe wall thickness is <NUM> (<NUM> inch) and the crest height of the buckle-inducing deformation is <NUM>% to <NUM>% of the first pipe wall thickness.

In another embodiment, a pipe joint arrangement comprises a first pipe comprising an end portion configured as a pipe spigot, and a second pipe comprising an end portion configured as a pipe bell. The pipe spigot is inserted into the pipe bell and welded to the pipe bell to seal the pipe joint between the pipe spigot and the pipe bell, and the first pipe comprises an outwardly-extending, buckle-inducing deformation that is spaced apart from the pipe bell of the second pipe.

The foregoing and other objects, features, and advantages of the disclosed technology will become more apparent from the following detailed description, which proceeds with reference to the accompanying figures.

Certain embodiments of the disclosure concern pipe joint arrangements and structural features that can be created in the pipes to induce buckling at a selected location spaced away from the pipe joint along the pipe axis. In certain embodiments, a pipe joint can be configured as a welded lap pipe joint between a first pipe comprising a spigot end and a second pipe comprising a bell, hub, or other increased diameter end portion configured to receive the spigot end of the first pipe. The bell/hub and spigot of the respective pipes can be welded together. In other embodiments, the first pipe and the second pipe can be butt-welded together. One or both of the first pipe and/or the second pipe can comprise an annular, buckle-inducing feature, referred to herein as a deformation, formed in the pipe and extending circumferentially around the pipe. The deformation is spaced apart axially from the pipe joint, and in particular from the welds of the pipe joint. The shape, height, and location of the deformations can be configured to provide strength in axial loading and bending during normal operation, reduce manufacturing complexity, and ensure that the pipe will buckle at the preselected location of the deformation well away from the welds of the pipe joint when subjected to a geohazard event such as an earthquake.

<FIG> illustrates a pipe joint arrangement <NUM> between a first pipe <NUM> and a second pipe <NUM> in a pipeline. In the illustrated embodiment, the pipe joint arrangement <NUM> is configured as a welded lap pipe joint arrangement in which a first end <NUM> of the first pipe <NUM> is received in a first end <NUM> of the second pipe <NUM>. The first end <NUM> of the first pipe <NUM> can be configured as a pipe spigot. The first end <NUM> of the second pipe <NUM> can comprise a hub or bell having a diameter D<NUM> greater than the diameter D<NUM> of the main body or main portion of the second pipe <NUM> (and of the first pipe <NUM>), and can be configured to receive the first end <NUM> of the first pipe <NUM>. The pipe joint arrangement <NUM> can comprise one or a series of welds indicated at <NUM> to join the pipes <NUM> and <NUM> together to form a pipe joint and seal the pipe joint. For example, in the illustrated embodiment the pipe joint arrangement <NUM> can comprise an internal fillet weld 20a joining the spigot end of the first pipe <NUM> to the interior surface of the bell of the second pipe <NUM>, and an external fillet weld 20b joining the bell end of the second pipe <NUM> to the exterior surface of the first pipe. In other embodiments, the pipe joint arrangement can include one of the fillet welds 20a or 20b, or more than two welds, depending upon the particular characteristics desired.

The first pipe <NUM> can comprise an increased diameter, buckle-inducing feature configured as a rib, bulge, raceway, ring, recess, concavity, or deformation <NUM> formed in the first pipe and projecting or extending outwardly from the first pipe. The deformation <NUM> is spaced apart from the pipe joint in an upstream direction. In certain embodiments, the deformation <NUM> can comprise an annular bulge or recess formed such that the outer diameter D<NUM> of the deformation is greater than the outer diameter D<NUM> of the first pipe, and such that the inner diameter D<NUM> of the deformation <NUM> is greater than the inner diameter D<NUM> of the first pipe. The deformation <NUM> can comprise a convex surface on the exterior of the pipe <NUM>.

The buckle-inducing deformation <NUM> is symmetric about the first pipe longitudinal axis <NUM>. For example, in certain embodiments the deformation <NUM> can be curved, and can have a constant or substantially constant radius (e.g., as measured relative to the longitudinal axis <NUM>). In certain embodiments, the deformation <NUM> can comprise a wave-shaped cross-section. <FIG> illustrates the contour of a representative embodiment of a deformation <NUM> from the apex or crest <NUM> of the deformation to the regular exterior surface of the pipe on one side (e.g., upstream of the crest). In <FIG>, the deformation <NUM> can be symmetric about the y-axis, and can have a contour shaped like a sine wave (e.g., on both the interior and exterior surfaces of the pipe). In certain embodiments, the contour of the deformation <NUM> can be curved or round (e.g., can have a substantially constant radius). <FIG> is a magnified partial cross-section showing one edge of a pipe <NUM> and an exemplary shape of another buckle-inducing deformation <NUM> formed therein. In other embodiments the radius, crest height, and/or the shape of the deformation can vary around the circumference of the pipe <NUM>. In yet other embodiments, the deformation can extend around only a portion of the circumference of the pipe <NUM>, for example, <NUM>%, <NUM>%, or <NUM>% of the circumference of the pipe. In still other embodiments, the deformation can comprise a compound curve shape, and can include multiple crests or apices of the same or different heights spaced apart by curved portions along the pipe axis.

In particular embodiments, the deformation <NUM> can be axially spaced from the bell <NUM>, and can be located at any location along the pipe axis between the ends of the pipe. In certain embodiments, the deformation <NUM> can be located close to the bell or hub of the second pipe, without interfering with the pipe joint or installation of the pipes. For example, in certain embodiments the crest <NUM> of the deformation can be axially spaced from the bell <NUM> (e.g., as measured from the edge of the bell portion <NUM>) by a distance L (<FIG>). The distance L can be, for example, <NUM> (<NUM> inches) to <NUM> (<NUM> inches) along the first pipe as measured from the edge of the second pipe <NUM> (or the weld 22b). In particular embodiments, the crest <NUM> of the deformation <NUM> can be axially spaced apart from the hub by <NUM> (<NUM> inches) to <NUM> (<NUM> inches), such as by <NUM> (<NUM> inches) to <NUM> (<NUM> inches), <NUM> (<NUM> inches) to <NUM> (<NUM> inches), at least <NUM> (<NUM> inches), at least <NUM> (<NUM> inches), or at least <NUM> (<NUM> inches), depending upon the particular characteristics desired and the equipment used to form the deformation. In certain embodiments, the crest <NUM> of the deformation <NUM> can be from <NUM> (<NUM> inches) to <NUM> (<NUM> inches), <NUM> (<NUM> inches) to <NUM> (<NUM> inches), <NUM> (<NUM> inches) to <NUM> (<NUM> inches), at least <NUM> (<NUM> inches), at least <NUM> (<NUM> inches), or at least <NUM> (<NUM> inches) from the outflow end <NUM> of the first pipe <NUM>.

In particular embodiments, the first and second pipes <NUM> and <NUM> each have a respective pipe wall, and the pipe walls of the first and second pipes can have a common thickness t in a direction perpendicular to the longitudinal axes of the first and second pipes, although in other embodiments the walls of the two pipes may have different thicknesses. The deformation <NUM> is symmetric about the longitudinal axis of the first pipe, and extends or projects outwardly from an outer surface of the first pipe by a projection distance or crest height x that is from <NUM>% to <NUM>% of the thickness of the pipe walls. In certain embodiments, the projection distance x is <NUM>% to <NUM>%, <NUM>% to <NUM>%, <NUM>% to <NUM>%, <NUM>% to <NUM>%, <NUM>% to <NUM>%, <NUM>% to <NUM>%, <NUM>% to <NUM>%, <NUM>% to <NUM>%, <NUM>% to <NUM>%, or <NUM>% to <NUM>% of the thickness of the pipe walls. According to the present invention, the projection distance x is <NUM> times to <NUM> times the thickness t of the first pipe wall.

In certain embodiments, the crest of the deformation <NUM> can be disposed or offset radially inwardly from the exterior surface of the second pipe <NUM> toward the axis <NUM>. In other words, in the illustrated configuration, the deformation <NUM> does not extend beyond the height of the exterior surface of the second pipe <NUM>, although the deformation may extend beyond the exterior surface of the second pipe in other embodiments.

In a particular embodiment, the thickness t of the pipe walls can be <NUM> (<NUM> inch) and the projection distance or crest height x can be <NUM>% to <NUM>% of the thickness of the pipe walls, such as <NUM>% to <NUM>%, or <NUM>% of the thickness of the pipe walls (or of the thickness of the first pipe at the location of the deformation). In certain embodiments, this combination of pipe wall thickness and crest height/projection distance can result in the axial strains induced at the spigot of the first pipe due to formation of the deformation being lower than the axial residual strains at the bell of the second pipe.

In another embodiment, the thickness t of the pipe walls can be <NUM> (<NUM> inch) and the projection distance or crest height x can be <NUM>% to <NUM>% of the thickness of the pipe walls, such as <NUM>% to <NUM>% or <NUM>% of the thickness of the pipe walls (or of the thickness of the first pipe at the location of the deformation). This combination of pipe wall thickness and crest height or projection distance can also result in the axial strains induced at the spigot of the first pipe due to formation of the deformation being lower than the axial residual strains at the bell of the second pipe.

In certain embodiments, the deformation <NUM> can be configured as an inwardly extending projection or rib (e.g., such that there is a recess created on the exterior diameter of the pipe). In other embodiments, the pipe can comprise more than one deformation, such as two deformations, three deformations, etc., (see <FIG>).

In certain embodiments, the deformation <NUM> can be formed by placing a mandrel or expander apparatus inside the first end portion or spigot of the first pipe <NUM>. The expander can comprise a push ring or other expansion device including an annular ring, rod, wire, cable, etc., disposed around the push ring. The annular ring can be pressed against the inner surface of the first pipe <NUM> (e.g., by expansion or radially outward movement of the push ring) such that the ring forms an impression or recess in the first pipe to form the deformation.

For example, <FIG> and <FIG> illustrate a representative embodiment of an expander apparatus <NUM> comprising a plurality of dies <NUM> arranged circumferentially around a spreader member or cone <NUM>. As best shown in <FIG>, the diameter of the cone <NUM> can increase along its length in a direction away from the dies <NUM>. Accordingly, by moving the dies <NUM> longitudinally along the cone <NUM>, the increasing diameter of the cone can move or urge the dies radially outwardly from the central axis of the expander.

Referring to <FIG>, the dies <NUM> can comprise extension portions or flanges <NUM> configured to contact the interior surface of a pipe disposed over the dies. The flanges <NUM> can comprise a length L and a free end portion <NUM>. Each die <NUM> can comprise a forming member or stamping member <NUM> configured as a curved rod, wire, cable, or other generally cylindrical member coupled (e.g., welded) to the free end portion <NUM> of the flange <NUM>. When the dies <NUM> are disposed on the expander, the forming members <NUM> can be arranged end-to-end in a generally circular shape. The length of the flange <NUM> and the position of the forming members <NUM> along the flange can be varied to vary the location of a deformation formed in a pipe.

To form the deformation, a pipe <NUM> (e.g., corresponding to the pipe <NUM> of <FIG>) can be positioned over the flanges <NUM> of the dies <NUM>. The cone <NUM> can then be moved for example, to the left in <FIG>, to advance the dies radially outwardly, thereby bringing the forming members <NUM> into contact with the inside surface of the pipe to form the deformation. The forming can be performed cold (e.g., at ambient temperature, without heating the steel), or with the pipe at elevated temperature, depending on the particular characteristics desired. The pipe <NUM> can also be subject to heat treatment following formation of the deformation.

<FIG> illustrates another embodiment of a system configured as a roll grooving machine <NUM> that can be used to form the deformation in the pipe. The roll grooving machine <NUM> can comprise a first rotatable die member <NUM> and a second rotatable die member <NUM> generally parallel to and vertically offset from the first die <NUM>. The second die <NUM> can comprise a rod or forming member <NUM> disposed circumferentially around a distal end portion <NUM> of the second die. The first die <NUM> can comprise a circumferential recess or groove <NUM> sized and shaped to receive the pipe wall as it is deformed by the forming member <NUM>.

In use, a pipe <NUM> can be disposed such that the first die <NUM> is located outside the pipe and the second die <NUM> is disposed inside the pipe. A hydraulic press of the system <NUM> can move the second die <NUM> downwardly such that the wall of the pipe <NUM> is pressed between the dies <NUM> and <NUM>, and such that the second die <NUM> and/or the forming member <NUM> engage the inside surface of the pipe. The first die <NUM>, which can be driven by a motor, can then be rotated. Rotation of the first die <NUM> can cause corresponding contra-rotation of the pipe <NUM> and of the die <NUM>. The forming member <NUM> can form the deformation by deforming the wall of the pipe <NUM> into the groove <NUM> of the first die <NUM>.

Although the pipe embodiments described above are particularly with reference to welded lap pipe joints, the pipe and deformation embodiments may also be used in other types of welded pipe joints, such as welded butt pipe joints. <FIG> illustrates a representative embodiment of a pipeline <NUM> including a plurality of pipes or pipe sections <NUM> joined together at butt joints, such as welded butt joints <NUM>. In certain embodiments, the pipe sections <NUM> can each comprise an outwardly-extending, buckle-inducing deformation <NUM> at a location along the length of the pipe section. The deformations <NUM> can be spaced apart from the welded butt joints <NUM> at any position along the pipe axis. Thus, the deformations <NUM> can be configured to induce buckling of the pipeline at location(s) spaced apart from the joints <NUM>, as described above. For example, in certain embodiments the deformations <NUM> can be spaced apart from the end portions <NUM> of the pipe sections (and/or from the edges of the joints <NUM>) by a distance D, which can be <NUM> (<NUM> inch) to <NUM> (<NUM> inches), <NUM> (<NUM> inches) to <NUM> (<NUM> inches), <NUM> (<NUM> inches) to <NUM> (<NUM> inches), <NUM> (<NUM> inches) to <NUM> (<NUM> inches), <NUM> (<NUM> inches) to <NUM> (<NUM> inches), at least <NUM> (<NUM> inches), at least <NUM> (<NUM> inches), at least <NUM> (<NUM> inches), etc. According to the present invention, the deformations have a crest height x that is <NUM>% to <NUM>% of the wall thickness t of the pipe sections <NUM>, and preferably such as <NUM>% to <NUM>%, <NUM>% to <NUM>%, <NUM>% to <NUM>%, or <NUM>% to <NUM>% of the wall thickness t of the pipe sections <NUM>, or any of the other crest height ranges described herein.

In the illustrated embodiment, the deformations <NUM> can be located near the ends of the pipe sections, but may be located anywhere along the length of the pipe sections. For example, in the illustrated embodiment the deformations <NUM> are proximate one end of the pipe sections <NUM> such that the deformations are closer to the weld at that end of the pipe section than the weld at the opposite end of the pipe section.

In certain embodiments, the deformations <NUM> can have a length dimension y measured along the axis of the pipeline <NUM>. The length dimension y can be from <NUM> (<NUM> inch) to <NUM> (<NUM> inches), such as <NUM> (<NUM> inches) to <NUM> (<NUM> inches), <NUM> (<NUM> inches) to <NUM> (<NUM> inches), <NUM> (<NUM> inches) to <NUM> (<NUM> inches), etc. In particular embodiments, the lengthy can be <NUM> (<NUM> inches).

In the illustrated embodiment, the deformations <NUM> are spaced apart by a distance L. In certain embodiments, the distance L can correspond to the length of the pipe sections <NUM>, such as <NUM> (<NUM> feet), <NUM> (<NUM> feet), <NUM> (<NUM> feet), <NUM> (<NUM> feet), <NUM> (<NUM> feet), <NUM> (<NUM> feet), etc. In certain embodiments, the deformations <NUM> can be spaced apart from each other at regular intervals, and/or at varying distances along the length of the pipeline depending upon the particular conditions and characteristics sought. In certain embodiments, the pipe sections can comprise more than one deformation <NUM>, such as two, three, or more deformations, which can be evenly spaced from each other or at any interval. In other embodiments, not every pipe section <NUM> need comprise a deformation <NUM>. For example, in certain embodiments every other or every second pipe section <NUM> can comprise a deformation.

In certain embodiments, a pipeline can comprise one or more relatively short pipe sections disposed between longer pipe sections. In such embodiments, the short pipe section can comprise one or multiple buckle-inducing deformations, which can be in relatively close proximity to the deformations at the end portions of the longer pipe sections. The overall effect can be to provide a plurality of buckle-inducing deformations in a relatively short distance. For example, <FIG> illustrates a pipeline <NUM> including a first pipe <NUM>, a second pipe <NUM>, and a third pipe <NUM> disposed between the first and second pipes, and which is shorter than the first pipe and the second pipe (e.g., <NUM>%, <NUM>%, <NUM>%, etc., of the length of the first pipe and/or the second pipe).

The first pipe <NUM> can comprise a buckle-inducing deformation <NUM> at the end portion adjacent the third pipe <NUM>, and the second pipe <NUM> can comprise a buckle-inducing deformation <NUM> at the end portion that is adjacent the third pipe <NUM>. The third pipe <NUM> can also comprise one or a plurality of deformations. For example, in the illustrated embodiment the third pipe <NUM> comprises a deformation <NUM> and a deformation <NUM>, although in other embodiments the third pipe can include more deformations (e.g., three or more deformations) or fewer deformations (e.g., one deformation or no deformations) depending upon the particular application.

The first pipe <NUM> and the third pipe <NUM> can be welded together at a first pipe joint <NUM> configured as a butt joint. More particularly, the ends of the first pipe <NUM> and the third pipe <NUM> can be welded (e.g., fillet welded) to a reinforcing member <NUM> configured as a butt strap extending between the first pipe and the third pipe, and encircling or enclosing the interface between the first pipe and the third pipe. One circumferential edge of the reinforcing member <NUM> can be welded to the exterior surface of the first pipe <NUM> at a fillet weld <NUM>, and the other circumferential edge of the reinforcing member can be welded to the exterior surface of the third pipe <NUM> at a fillet weld <NUM>. Fillet welds <NUM> and <NUM> can join the ends of the first pipe <NUM> and the third pipe <NUM>, respectively, to the interior surface of the reinforcing member <NUM>. In the illustrated embodiment the ends of the first pipe and the third pipe are spaced apart within the reinforcing member, although in other embodiments the ends of the pipes may contact each other. The opposite end of the third pipe <NUM> can be coupled to the second pipe <NUM> at a second pipe joint <NUM>, which can be configured similarly to the first joint <NUM>.

As noted above, the overall effect of the pipeline <NUM> can be to locate a plurality of buckle-inducing deformations within a short distance of each other along the pipe axis. This can allow the pipeline <NUM> to bend or flex about one or more of the deformations in the same direction, or in different directions. Such a pipeline can be particularly advantageous, for example, in applications where significant displacement of portions of a pipeline may occur, such as at the location where a pipe exits a building (due to settling), or areas prone to significant seismic activity or soil subsidence. The deformations of the first pipe, the second pipe, and the third pipe can be configured according to any of the deformation embodiments described herein. Any of the deformations can be configured similarly or differently from each other, depending upon the particular characteristics desired. For example, in certain embodiments one or more of the deformations can have different heights, lengths, curvatures, etc. In other embodiments, butt-welded pipe joints such as illustrated in <FIG> need not include reinforcing members, depending upon the particular requirements of the system.

Any of the pipe embodiments described herein can also comprise multiple buckle-inducing deformations in relatively close proximity to each other, not all of which need be configured the same. For example, <FIG> illustrates a representative example of a pipe <NUM> comprising two deformations <NUM> and <NUM> formed in one end portion. In the illustrated embodiment, the height of the deformation <NUM> is greater than the height of the deformation <NUM>, although in other embodiments the opposite may be true. The deformations <NUM> and <NUM> can also have the same height. The number of deformations is not limited to two, and the pipes described herein may include three, four, five, or more deformations, and the deformations can be of any size and can have any spacing.

One or more of the pipe, pipe joint arrangement, and/or deformation embodiments described herein can provide significant advantages over known pipes and pipe joint arrangements. As described in detail in the examples below, the deformations can be configured to initiate buckling of the pipe at a selected location spaced apart from the joint and/or from the bell or hub of the pipe (in the case of bell and spigot joints) along the longitudinal axis of the pipe. At the same time, pipe joints configured as described herein can withstand nearly the same bending, compressive, and/or tensile loading conditions as comparable joints between plain pipe without deformations.

More particularly, buckle-inducing deformations having dimensions within the ranges given herein can provide strength advantages and manufacturing advantages over existing systems, such as those designed around buckling wavelength(s) of the pipe. For example, recesses formed in pipelines in certain existing systems are sized according to buckling wavelengths or half wavelengths of the pipe. The height of these features tend to be many multiples of the pipe wall thickness (e.g., eight times the wall thickness to as much as <NUM> times the wall thickness). This means that the recesses must be formed in the pipe at high temperature, which is laborious and requires specialized equipment. In contrast, buckle-inducing deformations configured as described herein can be integrally formed in the pipe sections of a pipeline at ambient temperature, significantly reducing cost and complexity.

Regarding performance, pipe joint arrangements including buckle-inducing deformations as described herein can balance the ability to control the location at which the pipe buckles (e.g., during a seismic event) with the need to provide axial and bending strength. For example, embodiments of welded lap joints and butt joints where the pipes include deformations as described herein can withstand bending or buckling of more than <NUM>° away from the pipe axis without loss of pressure containment. Additionally, in certain embodiments, the joints can exhibit ultimate bending strength and ultimate axial strength of more than <NUM>% of the strength of comparable joints between plain pipe without a buckle-inducing feature.

For example, <FIG> illustrate the simulated performance of a series of exemplary welded lap pipe joint arrangements configured according to the embodiment of <FIG>. Each of the simulated pipes had a diameter of <NUM> (<NUM> inches), a pipe wall thickness of <NUM> (<NUM> inch), and was pressurized to <NUM>% of the yield pressure Py. The simulated pipe joint arrangement had buckle-inducing deformations of varying height. For example, the pipe joint arrangement represented by curve <NUM> in <FIG> had a deformation height of <NUM> times the pipe wall thickness t (<NUM>) (<NUM> inch). The pipe joint arrangement represented by the curve <NUM> had a deformation height of two times the pipe wall thickness, the pipe joint arrangement represented by the curve <NUM> had a deformation height of three times the pipe wall thickness, and the pipe joint arrangement represented by the curve <NUM> had a deformation height of four times the pipe wall thickness. The curve <NUM> is representative of a welded lap pipe joint arrangement with no deformation. The curve <NUM> is configured according to an existing system with a deformation height of <NUM> (<NUM> inches) (approximately <NUM> times the wall thickness t) based on a buckling wavelength of <NUM> (<NUM> inches), which is significantly larger than the deformations of the present disclosure.

<FIG> illustrates the normalized bending moment of the pipe joint arrangements versus the normalized curvature of the pipe joint arrangements. As shown in <FIG>, the pipe joint arrangement with a buckle-inducing deformation of <NUM>. 83t represented by curve <NUM> withstood nearly the same maximum bending moment as the pipe joint arrangement without a deformation represented by curve <NUM>, reaching a peak of approximately <NUM>/Mp at a curvature of <NUM>/kb before buckling (e.g., at the buckle-inducing deformation. The pipe joint arrangement with a deformation height of <NUM>. 83t displayed only limited curvature up to a bending moment significantly above <NUM>/Mp, while the existing pipe joint arrangement represented by curve <NUM> reached the same curvature of <NUM>/kb at a bending moment below <NUM>/Mp. Thus, the pipe joint arrangement of curve <NUM> withstood more than six times the bending moment of the pipe joint arrangement of curve <NUM> for an equivalent amount of curvature. Each of the pipe joint arrangements represented by curves <NUM>-<NUM> with deformation heights configured according to the embodiments described herein also withstood significantly greater bending than the pipe joint arrangement of curve <NUM> before buckling. This means that the pipe joint arrangements as described herein will continue to provide full or nearly full volume flow capacity at relatively high loads before buckling.

<FIG> illustrates simulations of the same pipe joint arrangements as <FIG> in compression loading. In <FIG>, the curve <NUM> represents the pipe joint arrangement with a deformation height of <NUM>t, the curve <NUM> represents the pipe joint arrangement with a deformation height of <NUM>t, the curve <NUM> represents the pipe joint arrangement with a deformation height of <NUM>t, the curve <NUM> represents the pipe joint arrangement with a deformation height of <NUM>t, the curve <NUM> represents the welded lap pipe joint arrangement without a deformation, and the curve <NUM> represents the pipe joint arrangement configured according to the existing buckling wavelength system with the deformation height of <NUM> (<NUM> inches) and the buckling wavelength of <NUM> (<NUM> inches). As shown in <FIG>, the pipe joint arrangement represented by the curve <NUM> withstood nearly <NUM>% of the yield force Fy before buckling, only slightly below the pipe joint arrangement <NUM> without a deformation. The existing pipe joint arrangement represented by the curve <NUM>, being configured to buckle when subjected to loading corresponding to ground waves of a specified wavelength, buckles at a substantially lower axial force of only approximately <NUM>% of the yield force Fy. In other words, the pipe joint arrangement configured according to the embodiments described herein with a buckle-inducing deformation with a height of <NUM>t withstood more than two times the axial compressive load of the pipe joint arrangement represented by curve <NUM>, and induced buckling at the predetermined location of the deformation. Pipes having a deformation with a crest height of five times (<NUM>%) of the pipe wall thickness would be expected to perform similarly to the pipe of curves <NUM> and <NUM> with a deformation height of <NUM>t.

Thus, the pipe joint arrangements described herein can provide surprisingly superior bending and axial strength advantages over known systems, while allowing the location of a buckle in the pipe to be preselected in the event of a geohazard incident. Accordingly, the pipe joint arrangements described herein can withstand significant deformation or buckling at the deformation feature without rupture, and without compromising the welds at the pipe joint or the seal between the pipes, allowing pipes such as municipal water pipes to continue to deliver water without loss of pressure containment.

In certain embodiments, the height of the crest of the deformation can also be configured to provide for a selected amount of lengthening of the pipe if the pipe is placed in tension (e.g., due to ground shifting).

The pipe embodiments described herein can be constructed from any of a variety of metallic materials, such as various steel alloys including, without limitation, ASTM A1011 SS GR36, ASTM A1018 SS GR40, ASTM A516, ASTM A572, ASTM A36, ASTM A283, and/or others listed in the American Water Works Association (AWWA) C200 Steel Water Pipe standard. Steel pipes having the diameter and thickness ranges described herein can advantageously be cold worked at ambient temperature to form buckle-inducing deformations having the dimensions and properties described herein, as well as bell end portions in the case of bell-and-spigot joints. Such forming processes can be carried out as described above at existing pipe mills, without the need for heating large sections of pipe. This can also provide improved strength because strength properties imparted to the steel pipes during rolling at the mill will be retained when the buckle-inducing deformation is formed at ambient temperature, and not lost during heating or annealing.

The pipes, pipe joint arrangements, and deformation embodiments described herein can be used for piping water, oil or gas, or other pressurized liquids or fluids. Such pipes can also be used for non-pressurized applications, such as conduits for carrying electrical conductors, fiber optic cables, etc..

Large-diameter continuous steel water pipelines with lap-welded pipe joint arrangements are often constructed in geohazard areas, where the pipeline may be subjected to severe transient (shaking) and permanent ground-induced actions. The experimental and numerical results presented herein concern <NUM>-cm(<NUM>-inch)-diameter pipes, with thickness equal to <NUM> (<NUM> inch) and <NUM> (<NUM> inch), indicated an excellent structural performance of the welded lap pipe joint arrangements: under compressive action, the ultimate strength (bending or axial) of the pipe joint arrangements has been found to be more than <NUM>% of the corresponding strength of the plain pipe, and - most importantly - the deformation capacity of the pipe joint arrangement has been remarkable: the pipe joint arrangement specimens have been bent to an angle that exceeded <NUM> degrees, without loss of pressure containment.

Nevertheless, there exists still some concerns among engineers and owners on the efficiency of lap welded pipe joint arrangements in seismic and other geohazard areas, mainly because of the presence of the "bell" and the fact that - in most of the cases - buckling of the pipe joint arrangement occurs at the bell, an area that has already been work-hardened and might be prone to fracture. The weld(s) at the bell may also be prone to fracture. The "seismic lap welded pipe joint arrangement" embodiments disclosed herein are aimed at improving the mechanical response of welded lap pipe joint arrangements, introducing a small initial imperfection/deformation at the spigot side of the weld, referred to as, for example, a "spigot imperfection," "seismic imperfection," or buckle-inducing deformation, in order to cause the buckle to occur at the spigot and prevent the formation of the buckle at the bell.

Numerical results on the structural performance of internally pressurized welded lap pipe joint arrangements, subjected to bending and axial compression on <NUM>-cm (<NUM>-inch)-diameter pipes, with two wall thickness; <NUM> (<NUM> inch) and <NUM> (<NUM> inch), are presented herein. In some embodiments an imperfection/deformation location, shape, and size at the "spigot" side of a lap pipe joint arrangement are proposed, to trigger buckling at the spigot rather than the bell. In certain embodiments, this "seismic imperfection" or deformation can be: (a) large enough to ensure that buckling will occur at the "spigot" pipe, while (b) small enough so that the structural strength of the pipe joint arrangement is not significantly reduced, compared to a lap pipe joint arrangement without an imperfection/deformation.

The present numerical results show that there can be an optimum size of this imperfection/deformation which can help to ensure that buckling occurs at the spigot and the structural performance of the lap pipe joint arrangement is not affected. Based on the present analysis, in certain embodiments, the optimum size of this imperfection/deformation can range between <NUM>-<NUM>% of the pipe wall thickness, such as <NUM>-<NUM>%. In practice, this imperfection/deformation can be imposed through a special wire around the expansion mandrel, and its size (amplitude or crest height) can be approximately equal to the pipe wall thickness.

Large-diameter continuous-welded steel water pipelines are usually constructed with lap pipe joint arrangements instead of butt-welded pipe joint arrangements, due to their lower construction cost. A welded lap pipe joint arrangement can comprise a "bell" cold-formed at the end of each pipe segment, using an expanded mandrel so that the end of the adjacent pipe segment, often referred to as "spigot", can be inserted and welded to the bell through a single or double full-circumferential fillet weld, as shown in <FIG>.

There exists a need for safeguarding the structural integrity of welded steel pipelines for water transmission, constructed in geohazard (seismic) areas. In those seismic areas, the pipeline may be subjected to severe transient (shaking) and permanent ground-induced actions from fault rupture, liquefaction-induced lateral spreading, soil subsidence, or slope instability. Any of these actions may deform the pipe well beyond the stress limits associated with normal operating conditions, possibly well into the inelastic range of the steel material.

The aforementioned experimental works, and the relevant numerical calculations, indicated an excellent structural performance of the welded lap pipe joint arrangements. More specifically, under compressive action, the ultimate bending strength of the pipe joint arrangements has been found to be more than <NUM>% of the corresponding strength of the plain pipe, and the deformation capacity of the pipe joint arrangement has been remarkable: the pipe joint arrangement specimens have been bent to an angle that exceeded <NUM> degrees, without loss of any pressure containment.

Nevertheless, despite the above excellent results, there exists still some concerns on the efficiency of lap welded pipe joint arrangements in seismic and other geohazard areas. The main concern refers to the pipe joint arrangement geometry, and the presence of the "bell". The bell is made by cold expansion that introduces significant work-hardening and residual stresses, and - because of its geometry - it imposes a "geometric imperfection" on the pipe, resulting in the formation of a local buckle at that location, associated with the development of high local strains that may lead to pipe wall rupture. Weld failure may also be a concern in certain situations.

It is possible to impose a small initial imperfection/deformation at the spigot side of the weld, in order to enforce the buckle to occur at the spigot, and prevent the formation of the buckle at the bell.

On the other hand, the above "initial imperfection" or "seismic" imperfection/deformation, desirably:.

To satisfy both requirements, a desirable or optimum configuration of the seismic pipe joint arrangement can be defined.

A large number of numerical simulations have been performed, which are summarized herein. In particular embodiments, an initial imperfection/deformation at the spigot is imposed as shown in <FIG>, which is similar to the deformation illustrated in <FIG>. One purpose of this analysis was to examine if the existence of the imperfection/deformation is capable of enforcing a buckling pattern with a local buckle at the spigot (preventing any buckle at the bell), while not affecting the structural strength of the welded lap pipe joint arrangement.

The present study evaluates the effect of the imposed "imperfection" or deformation at spigot side, in the structural performance of welded lap pipe joint arrangements both in bending and axial loading, for two levels of internal pressure (zero pressure and <NUM>% of yield pressure py). Two different pipes are analyzed, the first pipe has <NUM> (<NUM> inch) diameter, and a thickness equal to <NUM> (<NUM> inch). The second pipe has the same diameter but with thickness equal to <NUM> (<NUM> inch). The steel grade of the pipes is ASTM A1011 SS GR36 and ASTM A1018 SS GR40, respectively.

The main target of the present analysis is the definition and evaluation of imperfection/deformation location, size, etc., as described in section <NUM> above. Towards this purpose, the following issues were evaluated: the location of the imperfection/deformation, the shape of the imperfection/deformation, and the size (height) of the imperfection/deformation.

In certain embodiments, the location of the imperfection/deformation can be at the spigot, and its position can be chosen close to the pipe joint, according to the capabilities of the plant equipment. In certain expanders the pipe can be inserted <NUM> (<NUM> inches), which is <NUM> (<NUM> inches) from the outside weld. For the sake of completeness, one more case has also been considered for the position of the imperfection/deformation, namely <NUM> (<NUM> inches) from the outer cross section of the spigot pipe (<NUM> (<NUM> inches) from the outside weld).

The shape of the imperfection/deformation can be chosen according to the shape of buckling developed when a pipe is subjected to bending with presence of internal pressure. In certain embodiments, this can mean a "bulging" shape.

The size of the imperfection/deformation can be a challenging consideration. To satisfy both conditions above, an in-depth investigation is required. To quantify this analysis, the following criterion was adopted: "the axial strains induced at the spigot pipe due to the imperfection/deformation forming should be lower than the axial residual strains at the bell due to the bell formation". This has been the main feature of the analysis described in the next sections. <FIG> depicts the symmetric part of the shape of imperfection/deformation (for the thin pipe with <NUM> (<NUM> inch) thickness) with respect to the distance from the imperfection "crown". <FIG> illustrates a comparison of the shape obtained with the numerical simulation with the shape measured in the plant.

A numerical (finite element) model has been developed in ABAQUS®/standard to simulate the joint behaviour, including this "seismic" imperfection/deformation. The model comprises four (<NUM>) main parts, a pipe with a bell configuration, a pipe with an imperfection/deformation at a specific distance from the end cross section (spigot), the outside weld and the inside weld, as shown in <FIG>. The model employs four-node, reduced-integration shell finite elements, referred to as S4R, for the pipes and <NUM>-node solid "brick" elements for the fillet welds. The mesh is shown in <FIG>. The total length of the model is <NUM> (<NUM> inches). The gap size between the bell and the spigot is constant around the pipe and is equal to <NUM> (<NUM> inch), which is within the AWWA C200 requirements.

Initially bell expansion was simulated. The bell configuration was achieved by expanding the pipe end, using an appropriate mandrel (rigid body) <NUM> that moves outwards at the radial direction, as shown in <FIG>. Subsequently, the imperfection/deformation of deformation at the spigot side was imposed. The imperfection/deformation at spigot was achieved by expanding the pipe at a specified location using an appropriate mandrel (rigid body) <NUM> that moved outwards in the radial direction as shown in <FIG>, as performed in the plant.

Following the bell formation, the imperfection/deformation of the spigot was simulated. For the pipe with <NUM>-cm (<NUM>-inch)-diameter and a thickness equal to <NUM> (<NUM> inch), two cases were under consideration for the position of the deformation at spigot side. In the first case, deformation was imposed at <NUM> (<NUM> inches) from the end cross section (<NUM> (<NUM> inches) from the outside weld), and in second case the deformation was at <NUM> (<NUM> inch) from the end cross section (<NUM> (<NUM> inches) from the outside weld). For the <NUM> (<NUM> inch) thickness pipe, deformation was created at <NUM> (<NUM> inches) from the end cross section (<NUM> (<NUM> inches) from the outside weld).

After spigot formation, the spigot and the bell were connected with the weld parts using appropriate kinematic constraints, which ensured the continuity of the geometry. Kinematic constraints were employed as follows; a "tie" was used to connect the spigot and the welds, and a "rough contact" with "no separation" was employed to connect the bell with the welds.

Two reference points, located at each end of the model, were employed, which were coupled, in all six (<NUM>) degrees of freedom, in order to apply the desirable boundary conditions. In the case of pure bending, the rotation was induced at both far ends of the model as shown in <FIG>. In the second case, for the case of compression, the axial displacement was induced at the end cross section of the bell side, while the end cross section of the spigot side remained fixed, as shown in <FIG>.

To define the amplitude of the spigot imperfection/deformation the following criterion was adopted: "the axial strains induced at the spigot due to the "imperfection/deformation" forming should be lower than the axial residual strains at the bell pipe.

After an extensive parametric study, for the thin pipe (<NUM> (<NUM> inch) thick) the optimum amplitude of spigot imperfection/deformation has been found equal to <NUM>% of the pipe thickness. For the case of thick pipe (<NUM> (<NUM> inch) thick) the amplitude of imperfection/deformation at the spigot is equal to <NUM>% of the pipe thickness.

The results obtained from the numerical model refer to both axial load associated with axial deformation and to bending moment associated with pipe curvature. The "spigot imperfection" or deformation used in the analyses have the amplitude specified in the above section for the two pipe thicknesses. <FIG>, <FIG>, <FIG>, <FIG>, <FIG>, <FIG>, <FIG>, and <FIG> illustrate the results of finite element models of pipes and pipe joints including buckle-inducing deformations as described herein. Approximate stress values (MPa) at different locations of the pipes are represented by various dashed lines. The approximate stress values associated with the various dashed line types are given in legends accompanying the figures. In general, in axial loading and bending, the stress in the pipe walls increases in a direction toward the crests of the buckle-inducing deformations, and/or towards the bells of the pipes <NUM>.

<FIG> and <FIG> present the results from a pure bending analysis in the presence of internal pressure equal to <NUM>% of the yield pressure and the corresponding buckling mode. Three cases are examined, assuming an "imperfection" or deformation at <NUM> (<NUM> inches) from the outside weld, <NUM> (<NUM> inches) from the outside weld and a lap pipe joint arrangement without an imperfection or deformation at the spigot, in a pipe with a thickness of <NUM> (<NUM> inch). <FIG> illustrate the pipe joint arrangement in bending with the deformation <NUM> (<NUM> inches) from the outside weld. <FIG> illustrate the pipe joint arrangement in bending with the deformation <NUM> (<NUM> inches) from the outside weld, and <FIG> illustrate a comparable pipe joint arrangement with no deformation. As can be seen in <FIG>, without a deformation <NUM> formed in the first pipe <NUM>, the second pipe <NUM> buckles at the bell.

<FIG> and <FIG>present the results from axial compression analysis in the presence of internal pressure equal to <NUM>% of the yield pressure and the corresponding buckling modes. Two cases are examined, with imperfections/deformations at <NUM> (<NUM> inches) and <NUM> (<NUM> inches) from the outside weld, respectively. <FIG> illustrate the pipe joint in axial compression with the deformation <NUM> (<NUM> inches) from the outside weld, and <FIG> illustrate the pipe joint with the deformation <NUM> (<NUM> inches) from the outside weld.

<FIG> and <FIG> present results from a pure bending analysis without internal pressure and the corresponding buckling modes for a pipe having a thickness of <NUM> in. The position of the "spigot" imperfection/deformation is the same as in the case of bending in presence of internal pressure. <FIG> illustrate the results with the deformation <NUM><NUM> (three inches) from the outside weld. <FIG> illustrate the results with the deformation <NUM><NUM> (six inches) from the outside weld, and <FIG> illustrate the results where the pipe <NUM> has no deformation. As shown in <FIG>, without a deformation in the first pipe <NUM>, the second pipe <NUM> buckles at the bell.

<FIG> and <FIG> show results from axial compression analysis without internal pressure and the corresponding buckling modes for a pipe with a thickness of <NUM> in. Two cases are consideed for the position of the imperfection/deformation at the spigot pipe. The position of the imperfection/deformation is at <NUM> (three inches) (<FIG>) and <NUM> (six inches) (<FIG>) from the outside weld.

<FIG> present numerical simulation results for pure bending of a <NUM> (<NUM> inch) thickness pipe with a deformation and without a deformation at an internal pressure of <NUM>% of the yield pressure. In <FIG>, the deformation <NUM> is located <NUM> (three inches) from the outside weld.

<FIG> present numerical simulation results for pure bending of a <NUM> (<NUM> inch) thickness pipe with and without an initial deformation at the spigot, and without internal pressure. In <FIG>, the deformation <NUM> is <NUM> (three inches) from the outside weld.

<FIG> and <FIG> present numerical simulation results for axial compression loading of a <NUM> (<NUM> inch) thickness pipe with and without an internal pressure, and a deformation <NUM> (three inches) from the outside weld. In <FIG>, the internal pressure is <NUM>% of the yield pressure, and in <FIG> there is no internal pressure in the pipes.

The results above show that a size range of this imperfection/deformation exists which can ensure that buckling occurs at the spigot and the structural performance of the welded lap pipe joint arrangement is not affected. Based on the present analysis, in certain embodiments the size range of this imperfection/deformation can be between <NUM>-<NUM>% of the pipe wall thickness. In practice, this imperfection/deformation can be imposed through a special wire around an expansion mandrel, and its size can be close to the pipe wall thickness.

For purposes of this description, certain aspects, advantages, and novel features of the embodiments of this disclosure are described herein.

As used in this disclosure and in the claims, the singular forms "a," "an," and "the" include the plural forms unless the context clearly dictates otherwise. Additionally, the term "includes" means "comprises. " Further, the terms "coupled" and "associated" generally mean electrically, electromagnetically, and/or physically (e.g., mechanically or chemically) coupled or linked and does not exclude the presence of intermediate elements between the coupled or associated items absent specific contrary language.

In some examples, values, procedures, or apparatus may be referred to as "lowest," "best," "minimum," or the like. It will be appreciated that such descriptions are intended to indicate that a selection among many alternatives can be made, and such selections need not be better, smaller, or otherwise preferable to other selections.

In the description, certain terms may be used such as "up," "down," "upper," "lower," "horizontal," "vertical," "left," "right," and the like. These terms are used, where applicable, to provide some clarity of description when dealing with relative relationships. But, these terms are not intended to imply absolute relationships, positions, and/or orientations. For example, with respect to an object, an "upper" surface can become a "lower" surface simply by turning the object over. Nevertheless, it is still the same object.

Although there are alternatives for various components, parameters, operating conditions, etc., set forth herein, that does not mean that those alternatives are necessarily equivalent and/or perform equally well. Nor does it mean that the alternatives are listed in a preferred order unless stated otherwise.

Claim 1:
A pipe joint arrangement (<NUM>), comprising:
a first pipe (<NUM>) comprising a main body having a first diameter (D2), an end portion (<NUM>) and a first pipe wall thickness (t);
a second pipe (<NUM>) comprising an end portion (<NUM>);
the end portion (<NUM>) of the first pipe (<NUM>) being welded to the end portion (<NUM>) of the second pipe (<NUM>) to form a pipe joint and to seal the pipe joint between the first pipe (<NUM>) and the second pipe (<NUM>);
the first pipe (<NUM>) comprising an outwardly-extending, buckle-inducing deformation (<NUM>) that is spaced apart from the pipe joint in an upstream direction;
wherein a crest height (X) of the buckle-inducing deformation (<NUM>) is <NUM>% to <NUM>% of the first pipe wall thickness (t);
wherein a contour of the buckle-inducing deformation (<NUM>) is symmetric about a longitudinal axis (<NUM>) of the first pipe (<NUM>), convex or sine-shaped, and curved from a crest (<NUM>) of the buckle-inducing deformation (<NUM>) to a regular exterior surface of the main body of the first pipe (<NUM>) having the first diameter (D2); and
wherein the buckle-inducing deformation (<NUM>) is configured to ensure that buckling occur at the preselected location of the buckle-inducing deformation (<NUM>) of the first pipe (<NUM>) when the pipe joint arrangement (<NUM>) is subjected to a geohazard event.