Bending Stiffness Reducer for Brace to Hull Connection

Abstract

Semi-submersibles are subjected to loading from waves, causing racking, longitudinal shear and parallelogramming, or differential movement of the pontoons. The cyclic wave loading makes the various connections, where stress concentrations occur, susceptible to fatigue damage throughout the hull structure. This is most evident at the connections between the braces and the main hull structure. A revised brace to main hull connection with reduced bending stiffness is employed to reduce the moment being transferred from the brace to the hull, thereby reducing the bending stress and susceptibility to fatigue damage. This improved connection employs an internal member to transfer the loads between the brace and hull structure mainly as tension and compression. As a consequence of the improved fatigue performance, the structural weight of the connection can be greatly reduced, thus increasing the capacity with which the semi-submersible hull can operate.

Claims

1. A floating structure being capable of use offshore, with said floating structure being made up of components such as pontoons, columns and deck(s), and containing one or multiple slender members connecting some of the components to each other, and said slender member providing translational rigidity with minimal flexural rigidity at its end-connections through a flexible element.

2. A floating structure according to claim 1, wherein the slender member is comprised of structure capable of withstanding axial and transverse loads, fixedly attached at its ends to the larger components, thereby forming a connecting member, with at least one of its ends having a flexible element capable of bending, upon translation or rotation of one or more of the connected components.

3. A floating structure according to claim 2, with its flexible element having two ends, end one fixedly attached to said slender member, with end two fixedly attached to one of said components, said flexible element being centralized by a warping plane, intersecting said flexible element at approximately its mid-span, said warping plane acts as a gimbal, and is fixedly attached in a direction perpendicular to, or approximately perpendicular to, said flexible element to both said slender member and said component, at distinct diameters of said warping plane, such that said warping plane allows rotation of the slender member about the approximate mid-span of the flexible member, but prevents translation of said slender member in a direction perpendicular to the axis of said flexible element at the point of intersection between said warping plane and said flexible element.

4. A floating structure according to claim 2, with the slender member comprised of either a cylindrical member, tubular member, or an I-beam member, or a trusswork or any combination thereof.

5. The flexible element of claim 3 in which said flexible element is cylindrical, or planar, having a dimension in the direction of bending which is less than its dimension in its axis of bending.

6. The flexible element of claim 3 in which said flexible element is a forging, or cast, or welded, or bolted, or riveted or any combination of the aforementioned.

7. The flexible element of claim 3, in which said flexible element is made of steel, or titanium, or aluminum, or fiberglass, or carbon fiber or any combination of the aforementioned.

8. The warping plane of claim 3, in which said warping plane is comprised of plate, or of corrugated plate, or of two or more layers of plate, or any combination of the aforementioned.

9. The warping plane of claim 3 in which said warping plane is comprised of elastomeric elements which act alone or in combination with other structure affixed as in claim 1 to centralize and prevent movement of the said connecting member in any direction transverse to the axis formed by its points of attachment.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0029] So that the basic need fulfilled by and demands placed upon the brace can be better understood, the drawbacks of the prior art appreciated and improvement on and benefits from this invention revealed, a more particular description and invention embodiments is provided in the following figures, followed by their detailed description. It is to be noted, however, that the appended drawings illustrate only typical embodiments of this invention and are therefore not to be considered limiting of its scope, for the invention may admit to other equally effective embodiments.

[0030] FIG. 1 is a typical structural arrangement showing a semi-submersible in section view.

[0031] FIG. 2 is a typical structural arrangement showing a semi-submersible in section view, in a diagrammatic representation.

[0032] FIG. 3 is a typical structural arrangement showing a semi-submersible in profile view.

[0033] FIG. 4 is a typical structural arrangement showing a semi-submersible in profile view, in a diagrammatic representation.

[0034] FIG. 5 is the diagrammatic section view showing a depiction of the behavior of the brace members in pry, with the brace in tension.

[0035] FIG. 6 is the diagrammatic section view showing a depiction of the behavior of the brace members in squeeze, with the brace in compression.

[0036] FIG. 7 is the diagrammatic section view showing a depiction of the semi rolling and the brace behavior with fixed end connections, as the hull parallelograms.

[0037] FIG. 8 is a diagrammatic plan view, showing a depiction of the longitudinal racking displacement of the hull in quartering waves and brace behavior with fixed end connections.

[0038] FIG. 9 is an isometric view of the standard brace to hull connection in isometric view.

[0039] FIG. 10 is a profile section view showing axial plus bending loads at the standard brace to hull connection.

[0040] FIG. 11 is the diagrammatic section view showing a depiction of the semi rolling and the brace behavior with hinged end connections, as the hull parallelograms.

[0041] FIG. 12 is a diagrammatic plan view, showing a depiction of the longitudinal racking displacement of the hull in quartering waves and brace behavior with hinged end connections.

[0042] FIG. 13 is an isometric view of the improved brace to hull connection in isometric view.

[0043] FIG. 14 is a profile section view showing axial plus greatly reduced bending loads at the improved brace to hull connection

DETAILED DESCRIPTION OF THE INVENTION

[0044] Referring now to the invention in more detail, a typical structural arrangement is shown in FIG. 1, showing a semi-submersible in section view and FIG. 2, shows a semi-submersible in section view in a diagrammatic representation. A semi-submersible, or more particularly the main hull structure of a semi-submersible is typically composed of a series of pontoons 1, columns 2, and an upper box structure 4. The hull of the semi-submersible is buoyant, operating at a waterline 3 approximately as indicated. The main deck 5 structure varies in its arrangement depending upon the intended use of the semi-submersible such as drilling, oil production, construction support, accommodations, etc. The brace structure 6 is shown, in this case, the standard way with built-in, or fixed ends 7.

[0045] For better understanding, FIG. 3 shows a semi-submersible in profile view, showing the same elements as in the section view, pontoons 1, columns 2, operating waterline 3, deck box 4, main deck 5 and brace structure 6.

[0046] FIG. 4 shows the diagrammatic representation of the semi-submersible in profile view, showing pontoons 1, columns 2, operating waterline 3, deck box 4, and brace structure 6.

[0047] Throughout its life, a semisubmersible is subjected to global wave loadings which are resisted by the brace 6 working in concert with the deck or deck box 4. When the semisubmersible is in beam seas, the pontoons 1 are alternatively pried apart and squeezed together and rolled into a parallelogram shape, by the passing waves. To prevent undue bending moment at the column 2 to deck box 4 connection, the braces 6 are intended to take the tension 8 and compression 13 loads generated by the hull-wave interaction as depicted in FIGS. 5 and 6, respectively.

[0048] FIG. 5 shows the semi-submersible in diagrammatic section view to illustrate the tension loads 8 the braces 6 are intended to carry, which are tension loads 8 when the wave crest 9 is at the semi-submersible centerline 10, and the pontoons are pried apart 12. The brace 6 is deflected with the tension loads 8 in this scenario primarily down 11, with little bending induced in the brace to column connections 7.

[0049] FIG. 6 shows the semi-submersible in diagrammatic section view to illustrate the compression loads 13 the braces 6 are intended to carry, when the wave trough 14 is at the semi-submersible's centerline 10 and the pontoons are squeezed together 15. The brace 6 is deflected with the compression loads 13 in this scenario primarily up 16, with little bending induced in the brace to column connections 7.

[0050] Referring now to FIG. 7, as a wave 17 approaches, the semi rolls, the ring formed in section view by the deck box 4, columns 2 and horizontal brace 6 will parallelogram. The connection between the deck box 4 and columns 2 is rigid 18, and transmits moment 19 to resist the deflection. In the prior art, the connection between the brace and columns 7 is also rigid 20 and the deflection of the hull distorts the braces 6 into an S shape, with a radius of curvature at the connection 7 Rho, resulting in bending moment 21 at the brace to column connection 7. The maximum stress along the brace 6 is then seen at the brace to column connection 7. The cyclical nature of the bending due to wave loading makes the brace to column connection 7 susceptible to fatigue damage.

[0051] Because the deck box 4 is orders of magnitude stiffer than the braces 6, the deck box 4 resists this load, but the hull still suffers significant flexure. The braces 6 adapt to the slope of the columns 2 at their ends 7. This flexure, from the perspective of the horizontal brace 6 looks like vertical displacement of the brace ends 22, free to translate vertically but not rotate 20. This distorts the brace into an S shape in section view, creating bending moment in the brace 21. As a result, the brace is not a purely tension 8-compression 13 member, but a beam column, suffering bending moment 21 due the interaction of its fixed ends 7 and the inevitable hull deflection, in addition to either the tension 8 or compression 13 load.

[0052] Similarly, when the hull is in quartering seas 23, as shown in FIG. 8, the hull racks, which moves the two pontoons 1 longitudinally relative to one another 24, resulting in the brace 6 adopting an S-shape in plan view due to the rigidity of its end connection 20. This deflection is analogous to the deflection described in FIG. 7, however this form of hull deflection causes brace bending 20 in the horizontal plane.

[0053] These vertical 22 and longitudinal 24 deflections can be quite high and the parallelogramming and racking deflection induced brace bending 21 stresses are typically roughly equivalent to the brace axial stresses caused by prying 12 and squeezing 15. However, because the deck box 4 is orders of magnitude stiffer than the braces 6, reinforcing the brace ends 7 does not appreciably reduce the hull flexure, it only reinforces the braces 6 locally, attracting more bending moment 21 and adding weight and cost to the hull.

[0054] For minimum weight, the sole purpose of the brace 6 should be to resist the pry 12 and squeeze forces 15 on the pontoons 1 and columns 2, while the loads from parallelogramming, as shown in FIG. 7, and racking, as shown in FIG. 8, deflections of the hull should be resisted by the deck box 4.

[0055] FIG. 9 shows the standard brace 6 to hull 2 connection, where typically, a brace 6 with a large cross-section is connected 7 to the hull 2 and backed up with hull internal structure 25 to resist both the axial 26 and bending 27 loads, as shown in FIG. 10. With such a large cross-section for the brace 6, connected 7 to the hull structure 2, it is inevitable that the hull deflection induces large magnitude bending 27.

[0056] Clearly, what is needed is to decouple the brace 6 from bending due to hull deflection, as depicted in FIGS. 7 and 8, by reducing the bending stiffness of the brace 6 to hull 2 connection 7. In this way, the brace can be sized optimally, for tension 8 and compression 13 loads, without attracting bending moments 21 which do not significantly reduce those hull deflections.

[0057] FIGS. 11 and 12, in a way analogous to FIGS. 7 and 8 respectively, show how braces 6 free to rotate at their ends 7 do not induce bending 21 in the brace. As a result, they can be designed for almost pure axial tension 8 and compression 13, without being reinforced to withstand and attract bending moments 21. From FIGS. 11 and 12, it can be appreciated that the braces 6 do not adopt an S shape, but instead remain virtually straight, with their end moments 21 greatly reduced.

[0058] The following embodiment is considered to be the preferred means for achieving this invention. Other arrangements may exist, which reduce the bending stiffness of this connection, so are intended to be hereby covered by the disclosure of this invention.

[0059] The preferred embodiment of this invention is shown in FIGS. 13 and 14. In FIG. 13, it can be appreciated that the design begins with the full cross-section of the brace 6 but after transitioning through an outer band of increased thickness 29, for local strength, the cross-section is reduced conically through a conical transition piece 30 which attaches to the flexible element 33, which is of reduced cross-section 35. A central flexing element 33 is disclosed, with one end of the flexing element 33 fixed to the hull structure 25 and the other end fixed to the brace 6 as shown in FIG. 14. Owing to the minimal cross-section of this element 33, the structure of the brace connection has a reduced y (distance from the neutral axis to the extreme fiber of the element in bending) from that employed on the brace itself for a reduced moment attraction. This cylindrical flexing member 33, internal to the brace 6, has a high axial load 26 capacity allowing for the safe transfer of loading as tension 8 or compression 13, without attracting significant bending stresses 21 due to hull deflections. Pictorially, this is represented by the same axial loads 26, but greatly reduced bending loads 27. As a consequence, detailed analysis has proven that the backing structure 25 is also of less weight as it is withstanding primarily axial loads 26, rather than roughly equal amounts of axial stress 26 and bending stress 27.

[0060] To withstand transverse loads and to align the flexing element with its axial loads, the brace end is constrained from transverse translation by a Warping Plate 31, which can withstand angular deflection at the flex member 33, while behaving rigidly in a direction radial to the brace 6. The warping plate 31 can flex to accommodate angular deflection of the brace 6 about the center of pivot 34 at the flex element 33, mid-span, with minimum stress, due to it being relatively thin plate material, on the order of thickness of the rest of the hull in that area. At the same time, the warping plate 31 is very rigid to in-plane-shear, so maintains the brace 6 end, and consequently its central flex element 33, at the center of axial force 26 action and pivot center 34. The warping plate 31 also transmits any transverse loads imparted to the brace 6, into the hull structure 25 through the outer transition piece 32.