EP0051091B1

EP0051091B1 - Riser pipe assembly for use in production systems

Info

Publication number: EP0051091B1
Application number: EP80303869A
Authority: EP
Inventors: John M. Bohannon
Original assignee: Conoco Inc
Current assignee: ConocoPhillips Co
Priority date: 1980-10-30
Filing date: 1980-10-30
Publication date: 1986-02-26
Also published as: EP0051091A1

Description

This invention relates to riser pipe assemblies of the type comprising a fixed-bottom lower transition joint for a suspended pipe riser in an oil and gas production system.
U.S. Patent No. 3,976,021, issued to Blenkarn et al., shows at Fig. 10 a riser having a transition joint with a straight taper between the upper and lower surfaces of the joint. That transition joint is not fixed at either its upper or lower surface. Blerkarn et al. does not disclose a curvilinear taper or an optimal design for such a taper.
U.S. Patent No. 3,605,413, issued to Morgan, discloses a riser having a rigidity varying lower portion which interconnects with an upper portion. The lower or base portion is disclosed to be made of steel and to have a non-uniform rigidity or section modulus wherein the maximum is at the foot of the base portion which connects to the seafloor structure, and wherein the minimum is at the top of the base portion which attaches to the upper portion.
To meet such criteria, the Morgan patent indicates that the base structure comprises a plurality of segments with each segment having a different outer diameter and wall thickness relative to every other segment. Although each segment has a different outer diameter, each has the same inner diameter. Each of these sections is interconnected so that the lowermost section has the largest diameter and each successively higher portion has a successively smaller outer diameter. Also, at the point of interconnection of each section there is a taper which compensates for the different outer diameters of the connected segments. It is disclosed in the patent that such tapering could extend along an entire segment.
In addition to the varying diameter segments, the base portion comprises rigidity transition structures which prevent abrupt changes in the radius of curvature and act as stress transfer members between the upper portion of the riser and the upper sections of the base portion of the riser.
Although the Morgan patent does indicate a transition joint comprising elements having different outer diameters, it fails to indicate a joint which has an outer surface which is continuously tapered from the top to the foot of the joint. Furthermore, the Morgan patent fails to disclose an optimally designed transition joint which has a nearly constant resultant stress along the length of its structure.
U.S. Patent No. 3,794,849, issued to Perry et al., discloses a neutral buoyancy conductor connecting a floating power plant to stationary conductors which then connect the power plant to the shore. The neutral buoyancy conductor is indicated to have constant inner and outer diameters and to bend as a catenary to distribute stress resulting from various loads. The Perry et al. patent also discloses in its drawings vertical structures having continuously varying thicknesses from top to bottom. The specification indicates that these are poured concrete seawalls erected to form channels, but does not further define them.
As with the Morgan patent, the Perry et al. patent fails to show a transition joint which has a continuously varying outer diameter from top to bottom which is optimally shaped to have nearly constant resultant stress along the length of the joint.
Another patent of interest is U.S. Patent No. 3,559,410 issued to Blenkarm et al. which discloses ring-type stress relief members. However, this patent fails to disclose a longitudinally extending, continuously curvilinearly varying outer diameter transition joint which has nearly constant resultant stress along the length of the structure.
Still another patent of interest in U.S. Patent No. 3,512,811 issued to Bardgette et al. which discloses a jacket-to-pile connector which has a partially varying thickness wall attached between a jacket leg and a pile to transfer horizontal loads therebetween. This patent, however, fails to indicate a longitudinally extending transition joint having a constant inner diameter, but a curvilinearly varying outer diameter and further having a nearly constant resultant stress along the length of the structure.
Finally, U.S. Patent No. 1,706,246 issued to Miller discloses in its drawings vertical structures having a continuously varying or tapered outer surface. These vertical structures are walls which have linearly varying thicknesses from top to bottom. However, this patent fails to disclose optimum design criteria or any advantages for having the walls so tapered. Furthermore, this patent fails to disclose a transition joint having such a tapered contour.
Thus, there is known, for example from aforementioned US-A-3605413, a riser pipe assembly comprising a riser pipe string connectable at its upper end with a sea surface structure and being joined at its lower end to a transition joint, the transition joint being secured to and projecting upwardly from a supporting structure on the seal floor and having a central bore extending therethrough.
However, with assemblies of this type problems may be encountered owing to the severe stresses applied to the lower portion of the assembly or transition joint resulting from factors such as sea currents and movement of the platform to which the riser is connected at the sea surface. This problem is recognised in US-A-3605413, but the solution proposed therein is somewhat complex.
The present invention is characterised in that said transition joint has an annular top surface connected to said riser, an annular bottom surface connected to said supporting structure, and an outer surface joining said top and bottom surfaces which has a continuous curvilinear taper from the bottom surface to the top surface, the transition joint being solid between the central bore and outer surface thereof, and said curvilinear taper being such that for a given axial load, shear load and bending load at said top surface, the resultant stress of said transition joint is substantially constant along the length thereof between the top and bottom surfaces.
Thus, in accordance with the invention improved strength against the stresses applied to the assembly is provided, whilst at the same time the structure is such that there may be economy of materials and ease of manufacture.
In a preferred embodiment the top surface predetermined diameter is predetermined according to both the outer diameter of the structure to which the top of the transition joint will be connected and the materials of which the joint and connecting structures are made. The degree of taper at any point along the outer surface between the top and bottom surfaces is defined by a diameter across the structural member at that point, which diameter is defined by the following equation:
By defining the outer surface according to the above formula, the transition joint has a substantially constant maximum resultant stress along the entire length of the joint. This provides an optimum transition joint in terms of economy of materials and ease of manufacture while retaining the desired strength against the stresses placed upon the transition joint which result from the bending moments created by loads imparted to the structure from ocean currents, waves and platform motions.
An embodiment of the invention will now be described by way of example and with reference to the accompanying drawings, in which:

Fig. 1 is a schematic illustration of a transition joint according to the present invention in its preferred use environment;
Fig. 2 is an elevation view of the transition joint taken in section;
Fig. 3 is a top view of the joint;
Fig. 4 is a bottom plan view of the joint; and
Fig. 5 is a schematic illustration of the joint under a load.

Referring now to the drawings, Fig. 1 diagrammatically shows a transition joint 2 according to the present invention positioned in its preferred use environment as a lower transition joint for a pipe riser with a fixed bottom. The preferred embodiment of the transition joint 2 comprises high strength steel and has a length of approximately fifty feet. This length is considered to be preferred because it provides ease of fabrication and yet is long enough to retain the advantages of a theoretically optimum transition joint which would extend the entire distance between the ultimate points to be joined.
The transition joint 2 connects to a portion of a seafloor anchor base structure 4 which is positioned on a seafloor 6. The structure 4 includes, in part, a wellhead body and wellhead connector. The wellhead connector, to which the transition joint 2 connects at a base portion 8, may be either a hydraulically actuated connector or a threaded connector. It is at the base portion 8 that the bending moments resulting from loads on the transition joint 2 are the greatest, and thus this portion must be sufficiently large to withstand such stresses. The size and strength of the wellhead connector and the other components comprising the structure 4 are sufficiently larger than the base 8 of transition joint 2, so that base 8 may be considered to be fixed.
At the end of the transition joint 2 opposite the base portion 8 is a top portion 10. At the top portion 10 the loads are not as large as those at the base 8, so the top portion 10 need not be as large as the base portion 8. Also at the top portion 10 the transition joint 2 connects with a pipe string 12 which in the Fig. 1 schematic representation is preferably a 9 5/8" tie-back string or riser. Pipe string 12 and transition joint 2 comprise a riser pipe assembly.
The string 12 extends from the transition joint 2 upward to a surface platform 14. Platform 14 is a floating tension leg type platform. The string 12 connects with the platform 14-at a connection 16 which, in a preferred embodiment, is a tensioning jack.
Located with in the previously described subsurface structures is a transport string 18 which provides a means of access between the platform 14 and the region below the seafloor 6. In the presently described preferred embodiment the transport string 18 is a production riser which communicates the substances to be obtained from the subseafloor regions to the platform 14.
Completing the Fig. 1 schematic is a member 20 which is disposed on the platform 14 and which is associated with the transport string 18 for controlling the dispersement of materials to and from the transport string 18 at the surface platform 14. The member 20 is preferably a completion tree.
Referring now to Figs. 2, 3 and 4, a preferred embodiment of the transition joint 2 is shown. The transition joint 2 includes a structural member 30 which is defined by a first top planar surface 32, a second bottom planar surface 34, a third outer surface 36 and a fourth inner surface 38. Transition joint 2 is solid in the space defined between first, second, third and fourth surfaces 32, 34, 36 and 38.
The outer planar surface 32 is annular and has an outer contour which is defined by a predetermined diameter. This predetermined diameter is selected according to the diameter and composition of the string 12 with which the transition joint connects. Parallel to the top surface 32 is the bottom planar surface 34 which is also annular and has an outer contour which is defined by a diameter which is larger than the diameter defining the outer contour of the top surface 32. Top and bottom surfaces 32 and 34 are in spaced relation.
Longitudinally defining the structural member 30 are the outer surface 36 and the inner surface 38. The outer surface 36 extends between, joins to and circumscribes the outer contours of the top surface 32 and the bottom surface 34. The contour of the surface 36 has a curvilinear taper from the bottom surface 34 to the top surface 32. The inner surface 38 likewise extends between the top surface 32 and the bottom surface 34, but extends perpendicular thereto to thereby define a longitudinal bore through the structural member 30.
Referring now to Fig. 5, the tapered contour of the outer surface 36 will be described. Initially, it is noted that the taper is continuous along the entire length of the joint which thus makes the length of the tapered contour relatively greater than the longest cross-sectional diameter of the joint. Fig. 5 schematically represents the transition joint 2 under a load resulting from, for example, the ocean currents, waves or platform motions. These loads impart bending moments and other stresses to the joint 2 such as indicated in Fig. 5 by an axial tension load T, a shear load S and a moment M. A result of these stresses is a resultant stress which results both from the bending stress on the outer fibers along the length of the convex outer surface of the joint and from the tensile stress on the joint. In order to obtain an optimum transition joint the contour of the outer surface 36 is to be shaped in accordance with the present invention so that this resultant stress is nearly constant along the entire length of the joint. This is accomplished by tapering the outer surface 36 according to the following equation:
Applicant discovered this equation and its underlying parametric definitions by combining certain assumptions with certain analyses. The assumptions included the joint 2 being fixed at its base 8 as depicted in Fig. 1 and having a constant internal diameter as depicted by the bore defined by the inner surface 38. Furthermore, it was assumed that the joint 2 was of the same material as the string 12 and that the forces T, M and S were known.
Having made these assumptions, Applicant defined certain parameters as follows, then made the accompanying analysis:

T=tension, top of joint, Newtons
M=moment, top of joint, Newton-metres
S=shear, top of joint, Newtons
9=angle from vertical, top of joint, degrees
L=length of joint metres
d=inside diameter, metres
x=distance along riser, measured from top downward, metres
o=outer fiber total axial stress, Newtons/metres²
A_x=cross-sectional area at x, sq. metres
D,=outside diameter at x, metres
I_X=moment of inertia at x, metres⁴
T_x, M_x, S_x, θ_x=same as above, measured at point x

From beam small deflection theory:
Assuming T_x=T, the total moment at x (M_x) in terms of the top conditions is
By assuming that θ_X varies linearly with x, then
and from (3) and (4)
By letting
then
Now solving (2) for M_x and assuming T_x=T
Next, Equating (7) and (8) yields
By definition and standard formulae:

Upon substituting these definitions from (10) and (11) into (9) and simplifying:
By assuming that
and
then:
Regrouping equation (15) in terms of D_x yields
and letting
and substituting into (16) gives
Putting (18) into the standard cubic equation form of
results in
Thus for solution of the standard cubic equation in this situation,
In terms of these definitions in (20), the solution of (19) is
This solution when expanded to incorporate the underlying parametric definitions of b and y expresses the outer diameter at a point x along the length of the joint 2 in terms of distance x, known conditions of the forces at the top of the joint, and desired maximum stress a.
In expanded form, the expression for b is:
In the preferred embodiment of the present invention it was assumed that the joint 2 was made of the same material as the string 12. Under this assumption the value of the outer fiber total axial stress, o, should be such that D. at x=0 (i.e., at the top of the joint 2) equals the outer diameter of the string (or riser) 12. Thus, for D_x=o=D_(riser)' solving equation (15) for a and letting D_x=D_(riser) yields
By manufacturing the transition joint 2 having outer surface 36 tapered according to equation (21), the optimum transition joint of the present invention will be obtained. Such as optimum joint has the requisite strength at its large base for withstanding applied loads, yet is optimally tapered to maintain a nearly constant resultant stress along the entire length of the joint thereby retaining the required strength throughout the structure but providing optimum economy of material and ease of manufacture. Therefore, the present invention has overcome the failures of the previously cited references to provide an optimally designed and manufactured transition joint.
It will thus be seen that the present invention, at least in its preferred embodiment, overcomes the above-noted and other shortcomings of the prior art by providing a novel and improved transition joint. This joint is optimally constructed to withstand the loads applied to it in its ordinary use environment, and yet is economically and easily manufacturable because of its tapered contour whereby a nearly constant resultant stress comprising the outer fiber bending stress and tensile stress results along the entire length of the joint.

Claims

1. A riser pipe assembly for communicating a region of the ocean floor with a structure (14) on the sea surface in an oil and gas production system, the assembly comprising a riser pipe string (12) connectable at its upper end with a sea surface structure (14) and being joined at its lower end to a transition joint (2), the transition joint (2) being secured to and projecting upwardly from a supporting structure (4) on the sea floor and having a central bore extending therethrough, characterised in that said transition joint (2) has an annular top surface (32) connected to said riser, an annular bottom surface (34) connected to said supporting structure (4), and an outer surface (36) joining said top and bottom surfaces (32, 33) which has a continuous curvilinear taper from the bottom surface (33) to the top surface (32), the transition joint (2) being solid between the central bore and outer surface (36) thereof, and said curvilinear taper being such that for a given axial load, shear load and bending load at said top surface (32), the resultant stress of said transition joint (2) is substantially constant along the length thereof between the top and bottom surfaces (32, 33).

2. An assembly as claimed in claim 1 characterised in that the diameter of said outer surface (36) of the transition joint (2) is defined by:

where D_x=cross-sectional diameter at a distance x from said top surface (32),

where

σ=outer fiber total axial stress along said outer surface (36), in Newtons per square metre

d=inside diameter of said transition joint (2), in metres

T=tension at said top surface (32), in Newtons

M=moment at said top surface (32), in Newton-metres

x=distance along said outer surface (36) measured from said top surface (32) toward said bottom surface (34), in metres

S=shear at said top surface, in Newtons

L=Iength of said transition joint

8=angle from vertical said transition joint is at said top surface, in degrees

and

where

3. An assembly as claimed in claim 1 or 2 characterised in that the outer diameter of the top surface (32) of the transition joint (2) is equal to an outer diameter of the lower end of the riser pipe string (12), the transition joint (2) and the riser pipe string (12) being constructed from the same material.