TELESCOPICALLY ASSEMBLED MECHANICAL CONNECTOR

Abstract

A mechanical connector, including a telescopically assembled, Merlin™ Family Connector is provided with one or more sets of threads on substantially matching frustoconical surfaces of a pin and a box of the connector. Strengthening means are introduced involving at least one of: a mechanical stiffening arrangement on an outside surface of the box or a mechanical stiffening arrangement on an inside surface of the pin. The strengthening means provided may involve systems of arbitrarily oriented ribs and/or fairing surfaces. The mechanical stiffening arrangements may be integral with the box or the pin, or they can be separate external/internal strengthening arrangements, as applicable. They can be also essentially annular clamps that would have relatively regular shapes essentially conforming to the external or internal surfaces of the box or the pin, respectively. The above modifications can be introduced to traditional connectors and to connectors designed to transfer high torsional loads.

Claims

1. A telescopically assembled mechanical connector provided with a thread on substantially matching essentially frustoconical surfaces of a box and a pin, said substantially matching essentially frustoconical surfaces of said box and said pin extending essentially between two sets of nipple seals, whereas one said set of said nipple seals is located near an end of said box and another said set of said nipple seals is located near an end of said pin and whereas each said set of said nipple seals incorporates axially engaging, substantially cylindrical surfaces with an outside surface and an inside surface of a male substantially cylindrical annular segment interacting radially through a mechanism of a hoop stress with substantially matching surfaces of a substantially cylindrical annular cavity, whereas said sets of said nipple seals are used for sealing a cavity between said box and said pin; whereas: said telescopically assembled means assembled in a telescopic way, said telescopic way of an assembling means that during said assembling all points of said pin and/or said box substantially follow essentially straight lines that are essentially parallel to essentially coinciding axes of said pin and/or of said box; wherein said telescopically assembled mechanical connector provided with said thread on substantially matching essentially frustoconical surfaces of said box and said pin includes strengthening means involving at least one of: a mechanical stiffening arrangement on an outside surface of said box, or a mechanical stiffening arrangement on an inside surface of said pin.

2. The telescopically assembled mechanical connector according to claim 1, whereas the outside surface of the box is an outside stress diameter surface of said box.

3. The telescopically assembled mechanical connector according to claim 1, whereas the inside surface of the pin is an inside stress diameter surface of said pin.

4. The telescopically assembled mechanical connector according to claim 1, whereas the mechanical stiffening arrangements optionally include one or more stiffening ribs.

5. The telescopically assembled mechanical connector according to claim 1, whereas the mechanical stiffening arrangement on the outside surface of the box is essentially an annular stiffening clamp, which may or may not be essentially integral with said box.

6. The telescopically assembled mechanical connector according to claim 1, whereas the mechanical stiffening arrangement on the inside surface of the pin is essentially an annular stiffening clamp, which may or may not be essentially integral with said pin.

7. The telescopically assembled mechanical connector according to claim 1, whereas at least one of said box or said pin utilizes: friction welding, injection molding, 3-Dimensional printing, traditional welding fabrication.

8. The telescopically assembled mechanical connector according to claim 1, whereas at least one of said box or said pin is made of at least one of: a high strength steel, or a corrosion resistant alloy, or a titanium alloy, or an aluminum alloy, or a magnesium alloy, or a nickel based alloy, or a non-metallic material including a plastic material, or an essentially hyperelastic material, or at least one of said box or said pin utilizes at least one of a lining or a cladding or a weld overlay.

9. The telescopically assembled mechanical connector according to claim 1, wherein at least one of the mechanical stiffening arrangements is made of at least one of: a high strength steel, or a corrosion resistant alloy, or a titanium alloy, or an aluminum alloy, or a magnesium alloy, or a nickel based alloy, or a non-metallic material including a plastic material, or an essentially hyperelastic material; whereas said non-metallic material, including said plastic or said hyperelastic material optionally includes reinforcements with fibers, wires, a fiber-mesh or a wire-mesh.

10. The telescopically assembled mechanical connector according to claim 1, wherein said telescopically assembled mechanical connector includes an assembly/disassembly fluid remaining liquid during an assembly operation; and whereas after said assembly operation said assembly/disassembly fluid is allowed to solidify in an assembled condition of said mechanical connector, and remains essentially solid, thus becoming essentially a solid seal.

11. The telescopically assembled mechanical connector according to claim 1, that includes an assembly/disassembly fluid which is metallic or non-metallic.

12. The telescopically assembled mechanical connector according to claim 1, whereas the thread on the substantially matching essentially frustoconical surfaces of the box and the pin includes at least one of: an axisymmetric thread, a left-handed thread, a right-handed thread; and wherein said telescopically assembled mechanical connector includes a plurality of spline teeth designed to transfer torsional loads structurally.

13. The telescopically assembled mechanical connector according to claim 1, whereas the thread on the substantially matching essentially frustoconical surfaces of the box and the pin includes at least one of: an axisymmetric thread, a left-handed thread, a right-handed thread, and wherein said telescopically assembled mechanical connector includes a plurality of keys designed to transfer torsional loads structurally.

14. The telescopically assembled mechanical connector according to claim 1, whereas the thread on the substantially matching essentially frustoconical surfaces of the box and the pin includes at least one of: an axisymmetric thread, a left-handed thread, a right-handed thread, and wherein said telescopically assembled mechanical connector includes a plurality of shear pins designed to transfer torsional loads structurally.

15. The telescopically assembled mechanical connector according to claim 1, whereas the thread on the substantially matching essentially frustoconical surfaces of the box and the pin includes at least one of: an axisymmetric thread, a left-handed thread, a right-handed thread, and wherein said telescopically assembled mechanical connector includes one or more dog-clutch teeth designed to transfer torsional loads structurally.

16. The telescopically assembled mechanical connector according to claim 1, whereas the thread on the substantially matching essentially frustoconical surfaces of the box and the pin includes at least one of: an axisymmetric thread, a left-handed thread, a right-handed thread, and wherein said thread includes at least one of: said left-handed thread interlocking with said right-handed thread, said axisymmetric thread interlocking with said left-handed thread, said axisymmetric thread interlocking with said right-handed thread, said left-handed thread interlocking with a left-handed thread having a different pitch, said right-handed thread interlocking with a right-handed thread having a different pitch, designed to transfer torsional loads structurally.

17. The telescopically assembled mechanical connector according to claim 1, whereas whereas: loaded sides of said thread on said substantially matching essentially frustoconical surfaces of said box and said pin are defined as sides, an engagement of which prevents a disconnection of said telescopically assembled mechanical connector provided with said thread on said substantially matching essentially frustoconical surfaces of said box and said pin, unloaded sides of said thread on said substantially matching essentially frustoconical surfaces of said box and said pin are defined as those sides of said thread on said substantially matching essentially frustoconical surfaces of said box and said pin that are not said loaded sides of said thread on said substantially matching essentially frustoconical surfaces of said box and said pin, each of thread generatrix angles Θ1.sub.b, Θ2.sub.b, Θ1.sub.p, Θ2.sub.p is measured between a normal to an axis of said box or between a normal to an axis of said pin and a thread generatrix of said unloaded side of said thread on said substantially matching essentially frustoconical surfaces of said box and said pin or of said loaded side of said thread on said substantially matching essentially frustoconical surfaces of said box and said pin corresponding respectively: a box thread generatrix angle Θ1.sub.b is measured on said unloaded side of said thread on said substantially matching essentially frustoconical surface of said box, a box thread generatrix angle Θ2.sub.b is measured on said loaded side of said thread on said substantially matching essentially frustoconical surface of said box, a pin thread generatrix angle Θ1.sub.p is measured on said unloaded side of said thread on said substantially matching essentially frustoconical surface of said pin, pin thread generatrix angle Θ2.sub.p is measured on said loaded side of said thread on said substantially matching essentially frustoconical surface of said pin; wherein said telescopically assembled mechanical connector provided with said thread on said substantially matching essentially frustoconical surfaces of said box and said pin incorporates mismatching thread angles that result in increasing a normal contact pressure near a thread tooth tip and increasing an effectiveness of leak prevention; and wherein at least one of absolute values of: a thread generatrix mismatch angle |ΔΘ1|=|Θ1.sub.b−Θ1.sub.p|≥0.02°, or a thread generatrix mismatch angle |Δη2|=Θ2.sub.b−Θ2.sub.p|≥0.02°,

Description

BRIEF DESCRIPTION OF DRAWINGS

[0152] FIGS. 1 through 20 are provided to facilitate understanding of key features and key implementations of novel connectors.

[0153] FIG. 1 shows an exploded view of a novel connector utilizing spline torque transfer.

[0154] FIG. 2 shows a cross-section through one side of a novel connector utilizing spline torque transfer (shown in FIG. 1).

[0155] FIG. 3 presents a half view of a novel connector featuring a key torque transfer arrangement.

[0156] FIG. 4 shows a detail of a key interacting with a box of a novel connector.

[0157] FIG. 5 presents a half view of a novel connector featuring fitted pin torque transfer arrangement.

[0158] FIG. 6 shows details of fitted pins interacting with pins and boxes of novel connectors, one for each end of the interacting surfaces.

[0159] FIG. 7 depicts a detail of a novel connector assembled, whereas the dog-clutch torque transfer principle is utilized near the outside surfaces of the pin and the box. The dog-clutch teeth utilize the full material thickness available between the (metal) nipple seal region and the outside surface of the connector.

[0160] FIG. 8 depicts a detail of a novel connector in an exploded view, whereas the dog-clutch torque transfer principle is utilized near the outside surfaces of the pin and the box. The dog-clutch teeth utilize a part of the material thickness available between the (metal) nipple seal region and the outside surface of the connector.

[0161] FIG. 9 depicts a detail of a novel connector assembled, whereas the dog-clutch torque transfer principle is utilized near the inside surfaces of the pin and the box. The dog-clutch teeth utilize the full material thickness available between the (metal) nipple seal region and the inside surface of the connector.

[0162] FIG. 10 depicts a detail of a novel connector in an exploded view, whereas the dog-clutch torque transfer principle is utilized near the inside surfaces of the pin and the box. The dog-clutch teeth utilize a part of the material thickness available between the (metal) nipple seal region and the inside surface of the connector.

[0163] FIGS. 11a through 11z depict examples of schematic representations of many design implementations of novel connectors, most of which utilize the following arrangements for transferring torque structurally: [0164] the spline connection principle; [0165] the key connection principle; [0166] the fitted (shear) pin connection principle; [0167] the dog-clutch connection principle; [0168] the interlocking threads connection principle.

[0169] FIGS. 11a through 11y depict for the sake of example design implementations of the above listed torque transfer mechanisms used separately and in combinations. Variations in structural segment sequencing along the example connectors shown are also featured. FIGS. 11y and 11z depict stiffening arrangements of novel and known connectors, respectively.

[0170] FIG. 12 depicts schematically a segment of a novel connector that combines the dog-clutch and the fitted (shear) pin principles. The high torque capacity region is located near the external (metal) nipple seals and the torque bearing protrusions extend partly through the wall thickness of the box.

[0171] FIG. 13 depicts schematically a segment of a novel connector that combines the dog-clutch and the fitted (shear) pin principles. The high torque capacity region is located near the internal (metal) nipple seals and the torque bearing protrusions extend partly through the wall thickness of the pin.

[0172] FIGS. 14a through 14e depict an example detail half view of a relatively low pressure (LP) to medium pressure (MP) connector provided with novel structural modifications. Several examples of pin design details are featured.

[0173] FIGS. 15a through 15c depict example detail half views of LP to MP connector box designs provided with novel structural modifications.

[0174] FIG. 16 depicts an example detail half view of a novel relatively high pressure (HP) connector design featuring axisymmetric threads.

[0175] FIG. 17 depicts an example detail half view of a novel HP connector design featuring axisymmetric threads and shear fitted pins arranged near the outside nipple seals.

[0176] FIGS. 18a through 18c depict example design details of novel mechanical connectors.

[0177] FIG. 19 depicts schematically optional thread crest geometry modifications.

[0178] FIG. 20 depicts a detail of a novel connector box interacting with a pin featuring a novel use of an assembly/disassembly fluid solidified in cavities.

MODES OF CARRYING OUT THE INVENTION

[0179] The high structural torsional capacities of novel connectors are achieved by incorporating high capacity torque transfer components in the design of the connectors, while the high torsional fatigue life is achieved by optimally shaping and accurately finishing the surfaces of components that transfer high torques between the objects connected. The objects connected can involve pipe or tube segments and/or elements of offshore or onshore structures. The said novel connectors incorporate also structural elements typical to the design of the Merlin™ family connectors that provide them with high bending capacities, and wherever required also with high axial load capacities.

[0180] Several implementations of novel connectors are depicted on FIGS. 1 through 20.

[0181] Any connector according to this invention can be built out of metallic or non-metallic materials. That is reflected for sakes of examples on FIGS. 4, 6, 9, 10, 12, 13 and 20 by varying cross-section hatchings, with differing kinds of hatchings separated with pointed lines. On all other figures the uniform line hatchings used are understood to represent either metallic or non-metallic materials.

[0182] FIGS. 1 and 2 show a novel connector featuring spline torque transfer arrangement 160. FIG. 1 shows an exploded view of box 100 and pin 110, while FIG. 2 shows a cross-section through the same connector assembled.

[0183] It is noted that spline system (set) 160, 165 as shown in FIGS. 1 and 2 can be also incorporated in FIG. 3, FIG. 5, it can be combined with any of FIGS. 7 through 10 or with FIGS. 11a through 11c, 11e, 11f, 11k, 11s, 11t, 11w, 11y, 12, 13, 14a, 15a through 17, 18c and/or 20 similarly to the arrangement depicted for a sake of examples on FIGS. 11d, 11g through 11j, 11l through 11p, 11r, 11u, 11v and/or 11x, 11y, 14a through 14e, 15a through 15c and/or 16 through 20. All the above highlighted combinations of structural torque transfer principles represent feasible designs of novel connectors.

[0184] In addition to spline torque transfer arrangement 160 this connector implements typical Merlin™ family features that are well known to those skilled in the art. The assembly and disassembly of all novel connectors featured herein are similar and they are briefly outlined here by reference to FIGS. 1 and 2.

[0185] Most novel connectors featured can be assembled either simply by (telescopic) pushing the box and the pin together, or they may need to be assembled (telescopically) with the aid of fluid pressure contracting the pin and expanding the box, which is the principle well known to those skilled in the art. A disassembly is only feasible while using fluid pressure, thus reversing the most common assembly operation that also utilizes an assembly fluid. That is carried out similarly to the corresponding operational procedures relevant to the Merlin™ family connectors and some of their derivatives. The assembly/disassembly of novel connectors are reversible, i.e. they can be disassembled (telescopically) using fluid pressure and reassembled (telescopically) again. The (telescopic) assembly and/or the (telescopic) disassembly can be carried out above or below the water surface.

[0186] During a telescopic assembly or disassembly with the aid of fluid pressure the annular compartment along an essentially frustoconical interface between a box and a pin is pressurized, so that a radial expansion of the box and a radial contraction of the pin result in an enlargement of a radial gap between the box and the pin, so that thread tips of the interacting parts become clear of each other and the parts can be pushed together (or let to slide away from each other in a controlled way) while a considerable force caused by the ‘end cap’ pressure of the assembly/disassembly fluid attempts at all times to push the box and the pin away from each other. That happens without any, or substantially without excessive contact between the thread tips of the threaded surfaces of the box and the pin. As soon as the connector make-up overlap has been reached during an assembly, the fluid pressure is reduced the radial deformations of the pin and the box disappear, the excess fluid is let out, all the threads snap into their final design positions and the connector is made-up. The relative axial, telescopic movement between the box and the pin is guided by essentially cylindrical interaction surfaces of (metal) nipple seals that at all times seal the pressurized fluid compartment on its ends. A telescopic disassembly is the reverse of the telescopic assembly.

[0187] Important design considerations pertaining to selecting heights of protrusions and depths of grooves used in the Merlin™ family connectors at various axial locations of those connectors, as well, preferable taper angles at various locations as well as means to improve the telescopic assembly and/or disassembly operations with the use of hydraulic pressure are disclosed for example in U.S. Pat. No. 8,056,940 and those essentially apply to implementations of this invention described herein. Those design features, or their equivalents, can be optionally applied to these designs, where applicable.

[0188] Identically to the known Merlin™ family connectors, each novel, mechanical connector, including a telescopically assembled mechanical connector, is provided with a zero pitch angle, axisymmetric thread located on substantially overlying, substantially matching, substantially frustoconical surfaces 2 extending essentially between two sets of (metal) nipple seals 140. One of said sets of (metal) nipple seals 140 is located near an end of box 110 and the other said set of nipple seals 140 is located near an end of pin 100. It is known to anybody skilled in the art that each of said sets of (metal) nipple seals 140 incorporates telescopically engaging, substantially cylindrical surfaces with an outside substantially cylindrical surface and an inside substantially cylindrical surface of a male substantially cylindrical segment interacting radially through the mechanism of a hoop stress with substantially matching substantially cylindrical surfaces of an annulus of a substantially cylindrical cavity 5. Said substantially matching substantially frustoconical surfaces 2 have in general variable taper angles of lines 2a, 2b, 2c, 2d, 2e, 2f and 2g shown for a sake of examples on FIG. 2. Lines 2a, 2b, 2c, 2d, 2e, 2f and 2g extend along segments of said substantially matching, substantially overlying substantially frustoconical surfaces 2, as shown. Anybody knowledgeable in the art knows that taper angles of lines 2a through 2g are measured between the tangents to said lines 2a through 2g and the axis of the said connector. In particular line 2d shown along a segment of splines 160 features for a sake of example a zero taper angle, a precise value is impossible to determine from FIG. 1 or 2, and any variation within a small range or even within a greater range of taper angles, like up to those pertaining for example to line 2c or even line 2g do not affect the novelty of this invention. Anybody knowledgeable in the art is aware that thread pitch angles are zero by definition for axisymmetric threads along for example lines 2c or 2e. The thread pitch angles are always independent on a small or larger value of the local taper angle. Along spline segment 160 (line 2d) the thread pitch angles are essentially equal to 90°, see FIG. 1 and the description of FIGS. 11a through 11x.

[0189] It is obvious from this description that thread pitch angle α at a given point along a frustoconical surface is defined ac′

[00001]$\alpha =\underset{\mathrm{\Delta \phi }.fwdarw.0}{\lim }\left[\mathrm{atan}\left(\frac{2.Math.\Delta H}{\mathrm{\Delta \phi }.Math.D_h}\right)\right]$

where: [0190] Δφ—infinitesimally small interval of the connector azimuth angle measured in radians between the points at azimuth angle locations −0.5.Math.Δφ and +0.5.Math.Δφ from the point along the thread line, where angle α is being measured; [0191] ΔH—infinitesimally small axial distance along the connector span over (corresponding to) the above −0.5.Math.Δφ to +0.5.Math.Δφ azimuth angle interval measured in radians from the given point along the thread line at which angle α is being measured; [0192] DH—the pitch diameter of the thread at the point along the thread, where angle α is being measured.
Whenever pitch H of a thread is constant along a frustoconical surface of a connector (a most practical case and the most common mathematical representation), the above formula simplifies and:

[00002]$\alpha =\underset{\mathrm{\Delta \phi }.fwdarw.0}{\lim }\left[\mathrm{atan}\left(\frac{2.Math.\Delta H}{\mathrm{\Delta \phi }.Math.D_h}\right)\right]=\mathrm{atan}\left(\frac{H}{\pi .Math.D_H}\right)$

For zero thread pitch angle α, axisymmetric threads pitch H=0, therefore angle α is also zero. For left handed or right handed threads on a frustoconical surface H>0 and α>0, by definition. Whenever pitch H is constant along a frustoconical surface, angle α varies slightly, because D.sub.H varies along the connector. Wherever angle α is required to be constant along a thread line, pitch H has to vary accordingly by keeping the ratio of H to D.sub.H constant, see the relations above. For splines treated as special cases of threads, H is infinite and α=90°, because tan(90°) is infinite, see FIG. 1.

[0193] (Metal to metal) nipple seals 140 are used to seal a cavity between box 100 and pin 110 that is filled with an assembly/disassembly fluid at the stage when the connector is only initially assembled. Nipple seals 140 seal the said cavity, while the fluid is delivered through port 170. Fluid (hydraulic) pressure expands box 100 and ‘contracts’ pin 110 in the radial direction through the mechanism of hoop straining and meridional bending. The relation between the hoop stress(ing) σ and the hoop strain(ing) ∈ is known to anybody skilled in the art, because it is expressed by the Hooke's Law: σ=∈.Math.E, where E is the Young modulus. That enables the final assembly stroke in the axial direction that makes up the connection by engaging zero-pitch angle threads 150, 155 of box 100 and pin 110. Axisymmetric, zero-pitch angle grooves (threads) 150, 155 can engage only in the correct axial position due to the use of non-uniform axial spacings of thread 155. Axisymmetric, zero-pitch angle thread 150, 155 is responsible for the transfer of axial and bending loads as well as for the axial and radial pre-stressing of the connector. Excess fluid is removed through fluid outlet ports 130 near each end of the connector.

[0194] Novel connectors of high torsional and bending load capacity optionally, but quite often require precisely accurate azimuth angle orientations of box 100 relative pin 110. The azimuth orientation angles of box 100 relative pin 110 are modified by rotating pin 110 relative box 100 around the axis of the connector. In a case the azimuth assembly angle is specified, spline set (system) 160 (and optionally 165) can optionally engage only in the correct circumferential position due to the optional use of optional non-uniform angular spacings of trough 165 (and of the matching optional spline tooth, not visible) in the circumferential direction, so that the novel connector can optionally be assembled in only the prescribed design azimuth orientation. That is most often the case.

[0195] In the connector shown in FIGS. 1 and 2 spline system (set) 160 (optionally including spline 165) is arranged on cylindrical segments of box 100 and pin 110, which is optional and preferable, but splines can also be shaped along tapered surfaces, essentially matching the average local taper angles of the contact surfaces of box 100 and pin 110.

[0196] Similarly to splines used in machine engineering, splines 160 (and optional splines 165) can be parallel-sided, they can have involute shaped sides, they can have triangularly shaped spline teeth, they can have straight teeth interacting with involute shaped teeth, etc., as required. If necessary radial and circumferential pre-loads can be used by utilizing a required degree of interference fitting between spline teeth 160 (and optionally spline 165) of box 100 and pin 110. The latter is often the case depending on the design requirements, as it typically is in Merlin™ family connectors with regard to the axial and radial pre-loading. Spline teeth 160 (and optionally teeth 165) of the connector shown in FIGS. 1 and 2 are examples, any known spline geometries can be used.

[0197] Design features typically used for assembling/disassembling the connectors shown in FIGS. 1 through 20 are deliberately omitted from the drawings for simplicity. Annotations 15, 16 and 17 on FIG. 1 indicate options to use lining 15, cladding 16 and/or welding overlay 17 on any surface of the connector, as required by design conditions. Lining 15, cladding 16 and/or welding overlay 17 most often with Corrosion Resistant Alloys (CRAs) are shown on FIG. 1 for sake of example in a generic way, because those can be used on any surface of any novel connector shown on FIGS. 1 through 20, according to particular project requirements, as it is known with regard to prior art connectors.

[0198] FIG. 3 presents a half view of a novel connector featuring key 305 torque transfer arrangement. For simplicity only box 300 and pin 310 are annotated, the remaining design features shown are analogous to those already explained.

[0199] FIG. 4 shows a detail of key 305 interacting with box 300 of the connector in FIG. 3. Key 305 shown in FIGS. 3 and 4 is sunk in pin 310. Gap 307 is shown between outside face 302 of key 305 and the depth of the key groove provided in box 300. Axisymmetric, zero-pitch angle thread is designated with 350 and 355; 355 is pertaining to non-uniform axial spacing grooving designed to prevent accidental incorrect assembly. The longitudinal axis of key 305 shown is parallel to the average taper of the interacting surfaces of box 300 and pin 310 along the length of the key, which is preferred, but that does not need be the case in other designs.

[0200] The precise shape of the example outside face 302 of key 305 is impossible to see in the figures. In order to allow for some bending rigidity of key 305 during the final stage of the assembly, while box 300 and pin 310 flex in meridional bending because of a pressurization, groove 315 can be optionally provided. Groove 315 may not be required in cases when outside face 302 of key 305 is rounded to match the outside major diameters of the axisymmetric grooving of pin 310 (not shown in FIG. 4 and not annotated on FIG. 3). Rounding outside face 302 of key 305 is preferable, either to match the outside contour of major diameters of the axisymmetric pin grooving, or equal to the minimum value of the major diameter of the axisymmetric pin grooving along the length of key 305, so that the outside corners of key 305 (sides of outside face 302) never protrude outside of the contour of the adjacent grooving of pin 310. Key 305 is best interference fitted into its channel in pin 310, and preferably also (preferably loosely) bolted to pin 310 (optional screw not shown) or otherwise secured, in order to avoid a possibility of jamming during a disassembly or assembly of the connector. The sides of key 305 are preferably also interference fitted into the key channel in box 300.

[0201] In FIGS. 3 and 4 key 305 shown is double-rounded, but that is for the sake of an example only. Practically all types of key connections used in machine engineering can be used with novel connectors. Those include feather keys, square keys, flat keys, beveled keys, Woodruff keys, taper keys, etc.

[0202] The key inserts can be alternatively provided with circular, oval, elliptical, or other curvilinear cross-sections. It is noted, however, that more machine-connection-like key cross section shapes, like square or rectangular cross sections with only slightly rounded edges have higher bearing load capacities than have those provided by keys having circular or elliptical cross sections.

[0203] Depending on the torque capacity of the connector required for a particular design, multiple keys can be arranged around the circumference of the connector (multiple o'clock positions), which is preferably the case. Those keys can be arranged in one circumferential row, like in case of FIG. 3, 11f, 11l, 11r, 11w, 11x or/and 11y, with additional keys not visible, or in several rows (see schematic illustrations in FIG. 11e), in staggered rows or in irregular arrangements (see schematic illustration in FIG. 11f). It is noted that key system 305 as shown on FIG. 4 can be also incorporated in the design shown on FIG. 5, it can be combined with any of FIGS. 7 through 10 or with any of FIGS. 11a through 11d, 11g through 11k, 11m through 11q, 11s through 11v, 11x, 11y, 12, 13, 14a through 14e, 15a through 15c and/or 16 through 20. All the above highlighted combinations represent feasible designs of novel connectors.

[0204] In a case of an ‘off a shelf’, or retrofitted Merlin™ family connector being adapted to carry high torsional loads, it may be acceptable to sacrifice some of the original axial and even bending capacity of the connector in order to upgrade its torsional load capacity by adding systems (sets) of keys 305.

[0205] If required, keys 305 are optionally, but typically, arranged around the circumference in a non-uniform circumferential pitch or/and pattern, in order to assure the connector assembly with the prescribed azimuth orientation of box 300 relative pin 310.

[0206] FIG. 5 presents a half view of a novel connector featuring shear (fitted) pin 505 torque transfer arrangements. Multiple fitted pins sets 505 can be arranged around the circumference of the connector in the region of one of the connector ends or simultaneously in regions of both ends as it is shown on FIG. 5. The use of shear pins 505 simultaneously at both connector ends is preferable, because that limits frictional load differential between the interaction surfaces of box 500 and pin 510. Shear pins 505 can be arranged in a single row at each end, or in multiple rows (sets) that may or may not be staggered with regard to each other in the radial and/or circumferential direction(s), see for example FIG. 17. Only one row of shear pins 505 is shown near each end in FIG. 5, for the sake of an example. If required, shear pins 505 are optionally, but typically, arranged with a non-uniform circumferential pitch (spacing) or pattern in order to assure the connector assembly with the correct azimuth orientation of box 500 relative pin 510.

[0207] FIG. 6 shows details of shear (fitted) pins 505, 605 interacting with pins 510, 610 and with boxes 500, 600 according to this invention, one for each end of the interacting surfaces. The top detail depicted in FIG. 6 is that of the connector shown in FIG. 5; see the bottom right corner of FIG. 5. The bottom detail in FIG. 6 is that of another similar connector, note the differing dimensional proportions of box 600, pin 610 and fitted pin 605. In particular note circumferential groove 615 in the box that is used in order to increase locally the meridional flexibility of box 600. Similar grooves or systems of multiple grooves increasing locally the structural flexibility can be arranged in corresponding locations or in other regions of boxes and/or pins, in particular in the regions adjacent to (metal) nipple seals. Depending on particular design requirements those may be beneficial in any connector depicted on FIGS. 1 through 20 or otherwise discussed herein.

[0208] Connectors featuring fitted pins 505, 605 can be economical in design, retrofitted with shear fitted pins or otherwise adapted for particular design requirements, because shear pins 505, 605 or alike can be easily located in regions of relatively low structural loading. Holes to fit shear pins 505, 605 are relatively easy to drill, shim or/and tap if threads are required to whatever geometries may be selected. Typically interference fitting of shear pins 505, 605 or alike may be required depending on particular design needs.

[0209] Shear (fitted) pins 505, 605 can be optionally screwed into one of the parts being connected or/and bonded with an adhesive, see also FIGS. 12, 13, 17 and 18b. O-rings, metal ring seals or other sealing arrangements can be used in order to protect shear pins 505, 605 from seawater and from internal fluids, as applicable. CRAs, titanium alloys, aluminum alloys, magnesium alloys, nickel based alloys, steels, other materials, cladding with CRAs, weld overlaying with CRAs or encapsulating of interacting regions in protective resins, etc. can be used with novel connectors featured herein. It is noted that fitted pins 505, 605 as shown on FIG. 6 can be also incorporated in the designs shown on FIGS. 1 through 3, or they can be combined with any of FIGS. 7 through 10 or with any of FIGS. 11a through 11l, 11n, and 11s through 11v, FIG. 11x, 11y, 14a, 15a through 15c, 18c, 19 and/or 20. All the above highlighted combinations represent feasible designs of novel connectors.

[0210] FIG. 7 depicts a detail of a novel connector assembled. The dog-clutch torque transfer principle is utilized near the outside surfaces of pin 710 and box 700. Dog-clutch teeth 780, 706, 716 utilize the full material thickness available between the (metal) nipple seal region and the outside surface of the connector, which is not fully visible on the figure.

[0211] If required, dog-clutch teeth 780, as well as optional dog-clutch teeth 706 and 716, are typically arranged around the circumference in a non-uniform circumferential pitch or/and pattern, in order to assure the connector assembly with the correct azimuth orientation of box 700 relative pin 710. Optional teeth 706/716 have for that purpose optionally different circumferential dimensions than teeth 780 have.

[0212] FIG. 8 depicts in an exploded view a detail of a novel connector. The dog-clutch torque transfer principle is utilized near the outside surfaces of pin 810 and box 800. Dog-clutch teeth 880, as well as optionally differently dimensioned dog-clutch teeth 806 and 816 utilize a partial material thickness available between the (metal) nipple seal region and the outside surface of the connector.

[0213] It is known to anybody skilled in the art that long life torsional fatigue strength of circular cross-section components (like for example turbine shafts) is less sensitive to the working cross-section changes than bending fatigue is. However, for this application high torsional fatigue strength is important and the preferred designs utilize relatively large fillet radii 702, 802 and 712, 812 for the concave regions of component edges. In particular large fillet radii 702, 802 are used on FIGS. 7 and 8 for box 700, 800 concave edge regions and large fillet radii 712, 812 are used for pin 710, 810 concave edge regions. For convex edge regions the shapes are not critical for fatigue life and chamfers 704, 804 are shown for the convex edge regions of boxes and 714, 814 for the convex edge regions of pins, but fillets can be also used instead. High torsional load capacity arrangements 780, 880, as well as optional dog-clutch teeth 706 and 806, 716 and 816 shown can feature optionally non-uniform circumferential pitch of shapes 706, 806 and 716, 816 on boxes 700, 800 and pins 710, 810 respectively, in order to assure that the connector can be optionally assembled only in its prescribed azimuth orientation of pins 710, 810 relative boxes 700, 800, respectively.

[0214] FIG. 9 depicts a detail of a novel connector assembled. The dog-clutch torque transfer principle is utilized near the inside surfaces of pin 910 and box 900. Dog-clutch teeth 990, as well as optionally differently dimensioned dog-clutch teeth 996, utilize the full material thickness available between the (metal) nipple seal region and the inside surface of the connector, which is not fully visible on the figure.

[0215] If required, dog-clutch teeth 990, as well as optional dog-clutch teeth 996, can be optionally, but typically, arranged around the circumference in an optional non-uniform circumferential pitch or/and pattern, in order to assure the connector assembly with the prescribed azimuth orientation of box 900 relative pin 910. Optional teeth 996 can have for that purpose different circumferential spacing than teeth 990 have.

[0216] FIG. 10 depicts in an exploded view a detail of a novel connector. The dog-clutch torque transfer principle is utilized near the inside surfaces of pin 1010 and box 1000. Dog-clutch teeth 1080, as well as optional dog-clutch teeth 1006 and 1016, utilize a partial material thickness available between the (metal) nipple seal region and the inside surface of the connector.

[0217] If required, dog-clutch teeth 1080, as well as optional dog-clutch teeth 1006 and 1016, can be optionally, but typically, arranged around the circumference in an optional non-uniform circumferential spacing or/and pattern, in order to optionally assure the connector assembly with the prescribed azimuth orientation of box 1000 relative pin 1010. Optional teeth 1006/1016 have for that purpose different circumferential spacing than teeth 1080 have.

[0218] For applications where high torsional fatigue strength is important and the preferred designs utilize relatively large fillet radii 1002 and 1012 for concave regions of component edges. In particular large fillet radii 1002 are used for box 1000 concave edge regions and large fillet radii 1012 are used for pin 1010 concave edge regions. For convex edge regions the shapes are not critical for torsional strength and chamfers 1004 are shown for the convex edge regions of box 1000 and 1014 for the convex regions of edges of pin 1010, but fillets can be also used instead.

[0219] The design of the protruding teeth and matching hollows carrying torsional loads can be reversed between the boxes and the pins without affecting the functionality of this invention in the examples shown on FIGS. 7 through 10. A mixed reversed/not reversed design can also be used instead of that shown.

[0220] Connectors featuring the dog-clutch torque transfer arrangements can be economical in design for particular requirements, because torque transfer teeth 780, 706, 716, 880, 806, 816, 990, 996, 1006, 1016 can be easily located in regions of relatively low structural loading as shown in FIGS. 7 through 10, 12 and/or 13. Dog-clutch teeth arrangements like those shown in details on FIGS. 7 through 10 can be also incorporated for example in any of the designs shown on FIGS. 11a through 11m, 11o, 11q, 11s, 11u, 11v, and/or 14a through 20. All the above highlighted combinations represent feasible designs of novel connectors.

[0221] Whenever the torque transfer arrangements are located simultaneously on both ends [near both (metal) nipple seal systems in the same connector, novel connectors utilizing fitted pins 505, 605 or dog-clutch torque transferring teeth 780, 706, 716, 880, 806, 816, 990, 996, 1006, 1016 characterize with most of the torque being transferred through the connector structures, while largely by-passing those main contact surfaces between the boxes and the pins that transfer the axial and bending loads.

[0222] FIGS. 11a through 11y depict for the sake of example design implementations of torque transfer mechanisms featured used separately and in combinations. Variations in structural segment sequencing along the example connectors shown are also featured.

[0223] Example design implementations of novel mechanical connectors shown in FIGS. 11a through 11y provide differing load transfer functions between box 1100 and pin 1110 are separated longitudinally into segments (sets). Surfaces 1111 of frustoconical pitch diameters (averaged diameter) are depicted schematically with dashed lines. Those extend between (metal) nipple seals near each of the connectors, which are shown on FIGS. 11a through 11y with short lines parallel to the connector axes, but not annotated. Groove/protrusions systems (also referred to herein as grooving) along frustoconical surfaces 1111 are shown schematically with groups of thin continuous lines. In general, the taper angles of the frustoconical surfaces of box 1100 and pin 1110 vary along the lengths of the connectors. The same is in general the case with other connectors like those shown on FIGS. 1 through 20. Fitted (shear) pin systems (sets) are indicated with rows of hollow shapes with barbs. Dog-clutch tooth systems are shown with rectangular zig-zag lines.

[0224] Because generic families of connectors are represented only schematically on FIGS. 11a through 11y, the same generic annotations are used for simplicity on FIGS. 11a through 11y for all the generic components corresponding in connectors of differing designs: [0225] Known types of grooving (thread) providing static and fatigue transfer of axial and bending loads are annotated 1140 (axisymmetric, zero pitch angle, i.e. α=0°); [0226] Thread grooving featuring absolute values of pitch angles (fixed or variable) greater than 0° and smaller than 90° (0°<α<90°) according to this invention are annotated 1120 and 1121 for general left-handed and general right-handed threads respectively; additionally left handed threads and right handed threads that have pitches significantly differing (i.e. greater or smaller) from those annotated 1120 and/or 1121 used in the same connector are annotated 1125 and 1126, respectively. Groovings 1120, 1121, 1125 and 1126 combine the functions of transfer of axial, bending and torsional static and dynamic (fatigue) loads; pitch angles of left-handed or right-handed threads generally vary slightly along a frustoconical segment of the connector, while always satisfying 0°<α<90°, but for telescopically assembled connectors discussed herein they can undergo arbitrary variations along connectors or be in particular constant along a connector, if desired so (thus describing a conical helix, or concho-spiral), even though in general there may be no reason for keeping angle α constant; [0227] Spline (grooving) sets according to this invention that transfers torsional static and dynamic loads are annotated 1130 (absolute value pitch angles essentially equal to 90°, α=90°, because splines can be regarded as threads having infinite axial pitch; note that the tangent of 90° is infinite); [0228] Systems (sets) of keys used for torque transfer are annotated 1107 for keys arranged in circumferential rows and 1117 for axially staggered key patterns, or for keys distributed irregularly on surfaces 1111; [0229] Systems (sets) of fitted shear pins used for torque transfer are annotated 1150; [0230] Systems (sets) of dog-clutch teeth used to transfer torque and situated in the outside or in the inside abutment areas are annotated 1160.

[0231] The numbers and/or sequences of segment (set) types shown in any schematic view included on FIGS. 11a through 11z and their relative axial arrangements are incidental and these values/features can be modified arbitrarily without changing the type of implementation of this invention.

[0232] FIG. 11a depicts an example implementation of a novel connector featuring two segments with grooving (thread) type 1140 and one segment with left-handed grooving (thread) type 1120. The example shown in FIG. 11a equally represents its mirror image with a replacement of grooving (thread) type 1120 with right-handed grooving (thread) type 1121, as shown on FIG. 11k.

[0233] FIG. 11b depicts an example novel connector featuring two segments with grooving type 1140 and two non-zero pitch angle segments with thread types 1120 and 1121. Segment 1120 utilizes a left-handed thread and segment 1121 utilizes a right-handed thread.

[0234] FIG. 11c depicts an example novel connector featuring several segments with grooving (thread) type 1140, a segment with thread type 1120 and a segment with thread type 1121. Segment 1120 utilizes a left-handed thread and segment 1121 utilizes a right-handed thread.

[0235] FIG. 11d depicts an example novel connector featuring two segments with grooving (thread) type 1140, one segment (set) with spline grooving type 1130, a segment with thread type 1120 and a segment with thread type 1121 (see also FIGS. 1 and 2). It is understood that similar systems utilizing multiple spline sets (segments) 1130 can also be used in connectors featuring also segments type 1120 and/or 1121, in connectors utilizing only segments type 1140 and sets type 1130, see FIGS. 1, 2, 11g through 11j, 11l through 11p, 11r, 11x or/and 11y for examples.

[0236] FIGS. 11e and 11f depict example novel connectors featuring known type of axisymmetric, zero-pitch angle grooving 1140 that is utilized to transfer axial and bending loads between box 1100 and pin 1110 with key inserts 1107, 1117 essentially following local taper angles of the pitch diameter surfaces 1111 of box 1100 and pin 1110. Any geometrical shapes and types of key inserts 1107, 1117 can be used. It is noted however, that the key-grooves and the key-inserts need not necessarily follow the local taper angles in many similar connectors. They may or may not be arranged essentially in straight lines and in addition to being arranged essentially in axial (meridional) planes, they can also be arranged at non-zero angles to the said axial (meridional) planes of the said novel connector.

[0237] Although that does not necessarily need to be the case, it is preferred that key inserts have as slim design as possible, in particular in the radial direction of the connector. If feasible, the grooving used to insert the keys utilized in this invention should preferably not penetrate inside the material of box 1100 or pin 1110 deeper than grooving type 1140, or/and types 1120 or/and 1121 if also used in the same connector (see also FIGS. 3 and 4).

[0238] However, in particular where the length of the said connector is the issue, or when the axially symmetric grooving is very shallow, deeper grooving than that outlined above may need to be used with key grooving 1107, 1117 utilized in the said novel connectors. Shallow grooving 1107, 1117 may weaken bending load capacities of connectors only minimally.

[0239] Non-zero pitch angle thread segments 1120, 1121, while used separately would only allow a reliable torque transfer in one rotational direction, that which tightens the tapered thread. Applying a torque in the opposite direction would have unscrewed the connection. Both these facts are well known to those skilled in the art, because they are widely used in threaded connections, including for example tapered threaded drill-pipe connectors. However, in novel connectors the unscrewing of either thread 1120 or 1121 is prevented because of the interlocking with other types of grooving 1140, 1121, 1120, or/and 1126, 1125 respectively and novel connectors like for example those shown on FIGS. 11a through 11d, 11k, 11o through 11v, 11x and/or 11y are very effective in the transfer of torsional loads in both opposite rotational directions. In novel connectors featuring only segments with thread direction 1120 (see FIG. 11a) or 1121 (see FIG. 11k or/and 11q) the unscrewing is prevented by interlocking (via an axial load) with axisymmetric grooving 1140. On connectors that utilize non-zero pitch angle thread 1120 and 1121 (FIGS. 11b, 11c and 11d) thread 1120 is torsionally interlocked against the opposite thread, with grooving 1140 and in the case of the system shown in FIG. 11d spline set (system) 1130 helping additionally. Interlocking in the torsional load direction is also effected simultaneously with any other structural arrangements used optionally, or in order to increase the torque transfer capacities of novel connectors, see multiple examples shown and/or described herein.

[0240] FIG. 11g features spline (rows) sets 1130 arranged outside axisymmetric, zero pitch angle grooving 1140 arranged along interface 1111 of box 1100 and pin 1110.

[0241] FIGS. 11h through 11j feature each several spline (rows) sets 1130 arranged interchangeably between axisymmetric, zero pitch angle thread 1140 arranged along interface 1111 of box 1100 and pin 1110.

[0242] FIG. 11k depicts an example novel connector featuring two segments with grooving (thread) type 1140 and one segment with grooving (thread) type 1121. The example shown in FIG. 11k equally represents its mirror image with a replacement of grooving (thread) type 1121 with grooving (thread) type 1120, as shown on FIG. 11a.

[0243] FIG. 11l depicts an example novel connector featuring three segments with grooving (thread) type 1140, two segments (sets) of splines 1130 arranged between the segments of axisymmetric threads 1140 and key system 1107.

[0244] FIG. 11m depicts an example novel connector featuring four segments with grooving (thread) type 1140, three segments (sets) of splines 1130 arranged between the segments of axisymmetric threads 1140 and two systems of fitted shear pins at each connector end.

[0245] FIG. 11n depicts an example novel connector featuring four segments with grooving (thread) type 1140, three segments (sets) of splines 1130 arranged between the segments of axisymmetric threads 1140 and systems of dog-clutch teeth 1160 at each connector end.

[0246] FIG. 11o depicts an example novel connector featuring four segments with grooving (thread) type 1140, three segments (sets) of splines 1130, single segments of non-zero pitch angle threads 1120 and 1121 each, and systems of fitted shear pins 1150 at each connector end.

[0247] FIG. 11p depicts an example novel connector featuring four segments with grooving (thread) type 1140, three segments (sets) of splines 1130, single segments of non-zero pitch angle threads 1120 and 1121, a system (set) of fitted shear pins 1150 near the outside (metal) nipple seals and a system (set) of dog-clutch teeth 1160 near the inside (metal) nipple seals.

[0248] FIG. 11q depicts an example novel connector featuring two segments with grooving (thread) type 1140, one segment with right-handed thread 1121 and systems (sets) of fitted shear pins 1150 at each connector end. Example novel connector shown in FIG. 11r implements a combination of 5 structural torque transfer arrangements featured herein implemented in a single design.

[0249] FIG. 11r depicts an example novel connector featuring three segments with grooving (thread) type 1140, two segments (sets) of splines 1130, single segments of non-zero pitch angle threads 1120 and 1121 each, a system (set) of keys 1107, a system of fitted shear pins 1150 near the outside (metal) nipple seals and a system of dog-clutch teeth 1160 near the inside (metal) nipple seals. Example novel connector shown in FIG. 11r implements a combination of 6 structural torque transfer arrangements featured herein implemented in a single design.

[0250] FIG. 11s depicts an example novel connector featuring two segments each of non-zero pitch angle threads 1120 and 1121, four segments in total.

[0251] FIG. 11t depicts an example novel connector featuring single segments each of non-zero pitch angle threads 1120 and 1121 and a system (set) of dog-clutch-teeth 1160 arranged near the inside (metal) nipple seals.

[0252] Note that FIGS. 11s through 11v do not feature axisymmetric thread 1140, which is acceptable, because each of threads 1120, 1121, 1125 and 1126 also transfer axial and bending loads. In fact threads 1120, 1121, 1125 and/or 1126 can be used in novel connectors without a use of zero pitch angle segment(s), providing that they are interlocked with at least one of the other structural torque transfer sets: splines, keys, fitted pins, dog-clutch pins or even other segment(s) of thread 1125, 1126, 1120 and/or 1121 respectively (i.e. those in the same directions, i.e. same-handed, see FIGS. 11u and 11v), providing that they use sufficiently differing pitch angle values, so that torsional interlocking would occur. It is, however, preferred to use pairs of opposite-handed thread segments with thread interlocking in mind; opposite-handed pairs meant as pairing left-handed thread segments with right-handed segments and vice versa.

[0253] FIG. 11u depicts an example novel connector featuring a segment of right-handed thread 1121 and a same-handed, i.e. also right-handed segment of thread 1126 having a pitch angle differing from that of thread segment 1121.

[0254] FIG. 11v depicts an example novel connector featuring a segment of left-handed thread 1120 and a same-handed, i.e. also left-handed segment of thread 1125 having a pitch angle differing from that of thread segment 1120.

[0255] FIG. 11w depicts an example novel connector featuring three segments with grooving (thread) type 1140, a segment (set) of keys 1107, two systems (sets) of dog-clutch teeth 1160 at each connector end two systems (sets) of fitted shear pins 1150 at each connector end.

[0256] FIG. 11x depicts an example novel connector featuring three segments with grooving (thread) type 1140, two segments (sets) of splines 1130, single segments of non-zero pitch angle threads 1120 and 1121 each, a system (set) of keys 1107 and systems (sets) of dog-clutch teeth 1160 near each end of the connector. Example novel connector shown in FIG. 11x implements a combination of 5 structural torque transfer arrangements featured herein implemented in a single design, with a system of fitted (shear) pins not used.

[0257] FIG. 11y depicts an example novel connector featuring three segments with grooving (thread) type 1140, two segments (sets) of splines 1130, single segments of non-zero pitch angle threads 1120 and 1121 each, a system (set) of keys 1107, two systems (sets) of (fitted) shear pins 1150 and systems (sets) of dog-clutch teeth 1160 near each end of the connector. All but one sets of structural arrangements designed to transfer torque are optional. FIG. 11y also depicts schematically optional external 1170 and internal 1180 sets of stiffening arrangements according to this invention that can essentially be for example annular stiffening clamps.

[0258] FIG. 11z depicts an example known connector featuring five segments with axisymmetric grooving (thread) type 1140. FIG. 11z also depicts schematically optional external 1170 and internal 1180 sets of stiffening arrangements according to this invention that can essentially be for example annular stiffening clamps.

[0259] Optional external 1170 and internal 1180 sets of stiffening arrangements according to this invention can be split along one or more o'clock locations on their circumferences in order to assure an easy assembly, typically at some stage after the pins and the boxes are assembles telescopically. However, in particular with a use of boxes and/or pins made of essentially hyperelastic materials (like rubber, isoprene, neoprene, some other synthetic materials, etc.), it may be feasible to slide on outside or in inside the connectors continuous clamps that are not split along their circumferences. Sets of stiffening arrangements 1180 can have their inside diameters essentially the same as those of the connectors, which is shown schematically on FIGS. 11y and 11z.

[0260] Pitch angles of threads 1120, 1121, 1125 and/or 1126 should be selected carefully in the design. Large, close to 90° absolute values of those pitch angles are more effective in the transfer of torque and less effective in the transfer of the axial and bending loads, vice versa for small pitch angles approaching 0°.

[0261] FIG. 12 depicts schematically a segment of a novel connector combining the dog-clutch and the fitted shear pin principles. The high torque transfer region is located near external (metal) nipple seals 1285 and the torque bearing protrusions extend partly through the wall thickness of box 1200 and they match cavities in pin 1210.

[0262] Pins 1290 or 1295 are tight fitted in cavities of box 1200 and pin 1210. Pins 1290 can have uniform cylindrical shape or pins 1295 can be of a slightly tapered shape (not shown) that would not be visible on the drawing, if shown. Optionally, stepped fitted pin design 1291 can be used in various implementations of this invention, as shown on FIG. 12. Optionally pin segment 1291 and the box region where it is inserted can be threaded, as designated with annotation 1292 in order to highlight that option (see also FIG. 18b). In a case the stepped fitted shear pin shape is selected, the stepped pin nest, threaded or not threaded, can be located in pin 1210, or it can be located instead in the box 1200 part of the connector, if preferred so, without affecting the functionality of this invention.

[0263] FIG. 13 depicts schematically a segment of a novel connector between box 1300 and pin 1310 that combines optionally the dog-clutch and the fitted shear pin principles. The high torque transfer region is located near internal (metal) nipple seals 1395 and the torque bearing protrusions extend partly through the wall thickness of box 1300. Fitted shear pins are depicted in fully inserted and partly inserted positions 1390 and 1391, respectively. Remarks already provided with descriptions of other drawings also apply to FIG. 13.

[0264] FIGS. 14a through 14e and 15a through 15c show novel connectors designed for relatively low design pressures to medium pressures with an objective to considerably decrease the assembly/disassembly fluid pressures in comparison with those used typically in known Merlin™ family connectors. For known connectors the assembly/disassembly fluid pressures increase with the reduction of connector size—lower hydraulic pressures are used for larger diameter connectors. For example for a known, high pressure production riser Merlin™ family connector having OD=8.625″ (219.1 mm) the assembly/disassembly fluid pressure required is typically very high. The novel connector designs shown in FIGS. 14a through 14e and 15a through 15c have considerably smaller ODs than is the 8.625″ regarded at present as the minimum feasible for the designs of known Merlin™ family connectors. In spite of the above, thanks to the design modifications introduced it was possible to considerably reduce the assembly/disassembly pressures required, to the extent that it may even be practicable to use compressed gas as the assembly/disassembly fluid. At the same time it was possible to achieve the overall length of the connectors assembled between the weld necks, as shown on FIGS. 14a and 15a of the order of 75% of the tubing (piping) OD. The overlaps between the boxes and the pins were around 60% of the ODs of the tubing (piping). Depending on the design loading of novel connectors featuring similar geometries it may be feasible to decrease the numbers and the pitch of threads used, etc., which may allow to reduce the length to ODs ratios and the overlap to ODs ratios even further.

[0265] The structural stiffenings of novel connectors shown on FIGS. 14a through 14e and 15a through 15c are represented schematically as infinitesimally thin shells for clarity of geometries shown. Simultaneously with the achievements highlighted in the paragraph above considerable material and weigh savings were achieved, which may be advantageous in some applications.

[0266] Novel connectors shown on FIGS. 14a through 14e and 15a through 15c can be built conventionally (traditionally) by welding the stiffeners to the box and the pin, subdividing the fairing plate/screen into smaller panels and welding those to the webs. The hatchings through the mid-thicknesses of those meridionally-planar stiffeners 1431, 1432 shown in cross-sections are hatched as traditionally fabricated components. The preferred manufacturing method of novel connectors and their components shown in FIGS. 14a through 14e is 3D printing. In a case pin 1410 had been built using 3D printing, the hatchings of stiffeners 1431 and 1432 would have been the same as that of pin 1410.

[0267] Novel structural modifications introduced on FIGS. 14a through 14e and 15a through 15c are the following: [0268] Novel variations in the stress IDs 1411, 1511, tapering of the stress ODs 1415, 1515 of boxes 1400, 1500, or their approximations; [0269] Optional tapering of the inside (stress) diameters 1417 of pin 1410, or its approximation; [0270] Providing optional planar ribs 1421, 1521 and/or curved ribs 1523, 1524, 1525, optionally forming stiffening patterns like for example helicoidal pattern 1526, box pattern 1527 or honeycomb pattern 1528 on boxes 1400, 1500; [0271] Providing optional planar ribs 1431, 1432, 1433, 1434, 1435, 1436, 1437, 1438, 1439, 1440, 1441 and/or curved ribs 1455, 1456, 1457, optionally forming stiffening patterns like for example helicoidal patterns 1460, box pattern 1461, honeycomb patterns 1462, 1463 or other patterns 1464, 1465, 1466, 1467 on pin 1410; [0272] Introducing optional web stiffeners 1802, see also examples of other web stiffener arrangements feasible 1801, 1803, 1804, 1805, 1806 and 1807, see FIG. 18a. Web stiffener 1801 shown is double-sided, stiffeners 1802 through 1807 are shown as single-sided for the sake of examples only. A use of similar double sided web stiffeners or any other shapes meeting particular design objectives is also feasible. [0273] Fairing the IDs of the pins to constant design values with optional fairing plates or screens 1471, 1472, 1473 and 1474; [0274] Introducing stress relieving cut-outs 1481, 1482 and similar (shown, but not annotated) that also allow fluid flow across stiffeners; [0275] Adjusting distances between the ends of the threaded segments and inside and outside nipple seals in order to control the meridional bending stiffnesses of pins and boxes in those regions.

[0276] Optionally, but preferably in most cases cylindrical fairing plates 1471, 1472, 1473, 1474 can be provided with pressure equalizing holes, slots screens, etc., so that the fluid pressures are substantially the same in the flow and in the cavities formed by pin stiffeners and fairings. Design details can vary considerably depending on the fluid transported and wide ranges of design conditions. In particular pressure equalizing holes 1491 shown on FIGS. 15a and 15b may be suitable for tubing or piping connectors transporting gases with not too big flow transients. High pressure, flow and thermal transients, multiphase flow, a presence of solid sediments, draining requirements, etc. may require more and larger holes, slots or screens with wide ranges of solidity ratios. Hole or slot structural or thermal reinforcements like for example 1817 (FIG. 18b) may be required in cases of high pressure, flow and/or thermal transients.

[0277] For slender connector designs where reducing component weight is important the design of inside (and outside) nipple seal regions may require novel local connector wall thickness increase(s) near one or both ends like that depicted on FIG. 14a as 1403. External and internal structural reinforcements can be used in order to provide acceptable load paths, to optimize hoop stress loading, meridional bending stiffness and to prevent buckling during the assembly and/or in operation. Stiffening means arranged on the outside surface of said box can optionally include implementations featuring fiber reinforced plastic stiffenings of said box of said mechanical connector.

[0278] FIGS. 14a through 14d, 15b and 15c show for sake of examples single rows of honeycombs and/or box stiffeners. However, many more rows of sandwich stiffeners like those (in particular honeycombs of relatively smaller dimensions) could be used instead in their places, as it is often practiced in engineering. The webs corresponding would be more slender, the resulting straining of boxes and pins would be more uniform and even greater weight savings might result. The single row ‘sandwich’ stiffeners in FIGS. 14a through 14d, 15b and 15c are shown herein for example, because those are less typical in sandwich panel engineering. External sandwich panel fairings on box stiffeners (not shown) can be also used. All the above mentioned stiffener designs can also be used on novel high pressure connectors like those shown in FIGS. 16 and 17.

[0279] FIG. 16 depicts an example detail of a novel connector designed for relatively high design pressures and limited space available along the connector axis. The design shown features outside tubing or piping diameter considerably smaller than OD=8.625″ (219.1 mm). The ratio of the length of the connector assembled (between the weld necks, as shown) to the outside diameter of the tubing is just above 60% and the ratio of the box/pin overlap to the outside tubing diameter is around 40%. Again, with further design optimizations, a reduced number of threads, a smaller thread pitch, smaller heights of the thread teeth, etc. as governed by a particular design premise achieving even smaller length and overlap ratios might be achievable. The materials used for novel connectors featured herein, and in particular for those depicted on FIGS. 14a through 17 are also of importance. The use of very high strength materials, in particular where their elastic moduli are not very high may also help in achieving very high design parameters of novel connectors at relatively small piping or tubing diameters (for example titanium and some nickel based alloys). Because of the high design pressure and the objectives to minimize the overall and box/pin overlap lengths the assembly/disassembly pressure required is relatively high, consistent with those used in the known Merlin™ family connector technology.

[0280] Box 1600 features multiple tapers 1615 on its outside diameter and meridional ribs 1621. More complex rib patterns like those shown on FIGS. 15a through 15c and highlighted in a discussion corresponding can be also used, if required. Pin 1610 features inside (stress) diameter tapering 1617 or its approximation, and inside diameter fairing or screen 1671. Fairing 1671 can be optionally provided on the inside of pin 1610 with pressure equalizing holes or slots (not shown) in order to equalize pressure between the tubing (piping) and pin cavity 1675. The optional pressure equalizing holes or slots are required for most designs.

[0281] All the connector components shown are represented as solids on FIG. 16. This connector can be constructed using conventional technology or 3D printing. A printed connector is shown on FIG. 16.

[0282] FIG. 17 depicts an example of a novel HP connector design featuring axisymmetric threads and shear fitted pins 1790, 1795 are arranged in two staggered rows near the outside metal (nipple) seals. Basic design of the novel connector shown on FIG. 17 is similar to that shown on FIG. 16. Fairing 1775 is provided for sake of an example on an outside of box 1700. Fairings could be similarly provided on the outside of boxes shown on FIGS. 14a, 15a through 15c and/or on FIG. 16 as well as on an outside of a box of any novel connector introduced herein.

[0283] Pins 1790 or 1795 are tight fitted in cavities of box 1700 and pin 1710. Pins 1790 can have uniform cylindrical shape or pins 1795 can have a slightly tapered shape (not shown) that would not be visible on the drawing, if shown. Stepped fitted pin design is used in various implementations of this invention, as shown on FIG. 17, but a use of not-stepped pins is also feasible. Optionally, pin segment and the box region where it is inserted can be threaded, see 1792 on FIG. 18b. In a case the stepped fitted shear pin shape is selected, the stepped pin nest, threaded or not threaded, can be located in pin 1710, or it can be located instead in the box 1700, if preferred so, without affecting the functionality of this invention. Allen wrench (key) nest 1797 can be provided, see FIG. 18b, screwdriver slot, Phillips or torx nest, etc. can be used instead. All the connector components shown are represented as solids on FIG. 16. This connector can be constructed using conventional technology or 3D printing. A printed connector is shown on FIG. 17.

[0284] FIGS. 18a through 18c depict example design details of novel connectors.

[0285] FIG. 18a depicts several examples of web stiffeners that can be used at any location on any stiffener on novel connectors described herein. Stiffener examples are shown schematically as shells and they are mounted on a demonstration web 1808. Stiffener 1801 is a double sided stiffener, stiffener 1801 is a similar single-sided stiffener. Any other web stiffeners, shown or not shown can be single-sided or double-sided. Other examples shown are angle stiffener 1803, T-stiffener 1804, bulb plate stiffener 1805 (with the bulb shown as a solid component), undercut stiffener 1806 and double-undercut stiffener 1807.

[0286] FIG. 18b shows equalizing hole reinforcing ring 1817 and example fitted pins 1790 and 1795, which are described in the description of FIG. 17. Reinforcing ring 1817 can be used to strengthen a fairing plate or a screen in a case of pressure transients or/and it can be required because of pressure transients associated with high thermal transients. The materials used can be metallic or non-metallic (tungsten, cemented carbides, crystals like corundum, beryllium, diamond for non-oxidizing flows, etc.).

[0287] FIG. 18c depicts an example of a typical axisymmetric thread used on boxes 1800 and/or pins 1810, but it is also a relevant illustration regarding left-handed and/or right-handed threads, see further below. Thread generatrix 1820 is that on the loaded side of the thread on box 1800 and thread generatrix 1830 is that on the unloaded side of the tooth. The loaded sides are those that resist disassembly of a connector. Angle Θ2.sub.b is measured between the normal to the box or connector axis (coinciding) and generatrix 1820. Angle Θ1.sub.b is measured between the normal to the box or connector axis (coinciding) and generatrix 1830. Thread generatrix 1840 is that on the loaded side of the thread on pin 1810 and thread generatrix 1850 is that on the unloaded side of the tooth. Angle Θ2.sub.p is measured between the normal to the pin or connector (coinciding) axis and generatrix 1840. Angle Θ1.sub.p is measured between the normal to the pin or connector axis (again coinciding) and generatrix 1850. Angles Θ2.sub.b and Θ2.sub.p are typically greater than zero (preferably approximately halves of angles Θ1.sub.b and Θ1.sub.p), even though designs with angles Θ2.sub.b and Θ2.sub.p equal to or close to zero have been used. Angles Θ2.sub.b and Θ2.sub.p close to zero are superior structurally, but connectors featuring such angles can be very difficult or impossible to disassemble; assembling them can be difficult too. Known connectors typically use Θ2.sub.b=Θ2.sub.p and θ1.sub.b=Θ1.sub.p, which can also be the case in novel connectors. However, in many design cases novel connectors use mismatching thread angles that is to say Θ2.sub.b≠Θ2.sub.p and/or Θ1.sub.b≠Θ1.sub.p, see FIG. 19. The manufacturing tolerances on thread angles Θ1 b, Θ1.sub.p, Θ2.sub.b and Θ2.sub.p required should be very small (high accuracy required), and each few hundreds of a degree of thread angle mismatch makes a noticeable difference in thread tooth loading when an accurate Finite Element Analysis (FEA) is carried out. Therefore, conservatively connectors can be regarded as utilizing novel generatrix angle mismatches when any of the absolute values of mismatch angle |ΔΘ2|=|Θ2.sub.b−Θ2.sub.p| or that of mismatch angle |ΔΘ1=|Θ1.sub.b−Θ1.sub.p| is not smaller than 0.02°, but smaller or larger values like for example 0.01°, 0.02°, 0.05°, 0.075°, 0.1°, 0.125°, 0.15°, 0.175°, 0.2°, 0.25°, etc. . . . or even more than 0.35° can be selected for the above purpose.

[0288] The types of mechanical connectors of long torsional and bending fatigue life provided with tapering outside diameters of boxes with optional tapering inside diameters of pins or/and optional radial ribs are immaterial, all connectors described or/and disclosed herein can be provided with variable outside stress diameters of boxes, variable stress inside diameters of pins or/and optional ribs. In addition to the connectors similar to those depicted those shown on FIGS. 14a, 16 and 17 connectors depicted on FIGS. 1 through 11y can be also provided with variable outside diameters of the boxes, tapered outside stress diameters of boxes (or their approximations), with optional variable or tapered inside stress diameters of pins (or their approximations) or/and optional ribs. The said novel variations and/or tapering of stress diameters are not limited to those depicted on FIGS. 14a through 17. In particular the taper angles can vary along the boxes and/or pins in order to provide hoop stress and meridional bending flexibility distributions along of the boxes and/or pins optimal for any particular application examples shown on FIGS. 14a through 17 were selected because they feature meeting design requirements that tend to fall on technically demanding sides.

[0289] FIG. 19 depicts schematically a detail of a cross section of interacting threads of box 1900 and pin 1910. Optional tooth crest geometry modifications that result in interference fit are shown exaggerated.

[0290] The typical radial interference fit between box 1900 and pin 1910 results in normal contact pressures between tooth surfaces 1920 and 1950 of pin 1910 as well as 1930 and 1950 of box 1900, respectively. As already highlighted above, the above mentioned radial interference fits are illustrated in exaggeration on FIG. 19, with the thread side annotations indicated respectively. Thus, FIG. 19 illustrates in exaggeration the interference fit of the unloaded sides 1920 of the pin and 1930 of the box and it also illustrates in exaggeration interference fit between the loaded sides 1950 of the pin and 1940 of the box.

[0291] In addition to the ‘regular’ radial interference fit of the thread, a design of additional, superimposed interference fits as illustrated schematically on FIG. 19 is preferably carried out so that the material stressing of box 1900 and pin 1910 remains essentially in the elastic range. For axisymmetric threads, thread mismatch angles ΔΘ1 and ΔΘ2 are in the meridional planes of the connectors, as shown in exaggeration on FIG. 19. For threads featuring non-zero pitch angle values, thread mismatch angles ΔΘ1 and ΔΘ2 are defined analogously to the above, but the thread mismatch angles are measured in planes normal to crest lines of the threads. Using generatrices on unloaded and loaded sides of teeth while defining the above angles assures that those angles are always measured in planes normal to crest lines of the threads. With a novel thread mismatch angle between the generatrix of surface 1920 and the generatrix of surface 1930 ΔΘ1>0, an increase of normal contact pressure near tip 1970 of tooth of the thread on pin 1910 results in comparison with the corresponding normal contact pressure distributions in known designs, i.e. those featuring the radial interference fit only. With a novel thread mismatch angle between the generatrix of surface 1940 and the generatrix of surface 1950 ΔΘ2>0, additional increase of normal contact pressure near tip 1970 along other parts of surfaces 1920, 1930, 1940 and 1950 result. Whenever thread mismatch angle ΔΘ2 is greater than approximately thread mismatch angle ΔΘ1 the interference fit results also in bending and shear of tooth of pin 1910 that is defined by surfaces 1930, 1950 and tooth tip 1970. With slim designs of pin teeth the said bending may also be effective whenever thread mismatch angle ΔΘ1≈0, or is negative (under the absolute value symbol). Axial interference fit between surfaces 1940 and 1950 against interference fit between the outside contact abutment surfaces is therefore affected by the said radial interference fits. Essentially elastic bending of teeth interacting results in more even axial and/or bending load distributions along connectors than those that would have taken place for angles ΔΘ1=ΔΘ2=0 due to the resultant decrease in the spring stiffness of the threads. This effect is more pronounced for ‘slim teeth’ threads (and relatively small axial spacing), than it would be for threads utilizing a greater axial spacing. FIG. 19 illustrates teeth interaction geometries featuring essentially rectilinear generatrices of contact surfaces 1920, 1930, 1940 and 1950, however in general cases some or all of the said generatrices can be curvilinear for more accurate control of normal contact pressure distributions along the contact surfaces.

[0292] It is well known that end teeth take most of the loading on threaded connections. For novel connectors designs featuring relatively smaller design pressures, smaller axial loads and/or smaller bending loads than those typically specified for connectors used on production risers offshore, using less thread teeth may be acceptable. Thread angle mismatching results in improved, more uniform thread loading along the connector. That is because of the smaller spring constant of a smaller axial spacing, slimmer teeth. Denser grouping of greater axial spacing teeth near the ends of the thread helps additionally, because of greater spring stiffnesses of those teeth than are those of a regular axial spacing teeth. In such arrangements more of the load of the regular end teeth is transferred to nearby teeth featuring increased axial spacing, see the thread on pin 1810, FIG. 18c, where only 3 ‘slim’ teeth are used between the end ‘thick’ tooth and the next ‘thick’ tooth. Similar approach was utilized in the designs shown on FIG. 14a, 15a through 15c, 16 and 17, in all cases on both thread ends.

[0293] Maximum contact pressures in regions of pin tooth tip 1970 increase the effectiveness of leak prevention along the surfaces interacting of box 1900 and pin 1910. In cases where temperature gradients exist along the connector, heat transfer coefficient (according to the Fourier Law) across the contact surfaces is higher where higher contact pressures occur. Other important factors affecting the heat transfer are for example the roughness and the waviness of the contact surfaces as well as film heat transfer coefficients (conduction, convection and radiation, whichever applies) of fluids, vacuum (or solids, see FIG. 20) filling voids and gaps between the contact surfaces.

[0294] Whenever the tooth crest shape modification principle illustrated on FIG. 19 is reversed (increased contact pressures in the region of box tips 1960, not shown on drawings) similar crest shape modifications would have similar positive effect on leak-proofing, but the structural effects would be decreased, because there is normally a gap between the inside abutment surfaces. However, the said reversed tooth crest shape modification principle may enhance heat transfer between pins and boxes in installations where connector pins 1910 tend to be hotter than connector boxes 1900.

[0295] FIG. 20 depicts a detail of connector box 2000 interacting with pin 2010 featuring a novel use of assembly/disassembly fluid 2025 solidified in cavities. According to one implementation of this principle, after an assembly at an elevated temperature with the assembly/disassembly fluid liquid (molten if it is metallic), the connector is cooled in a controlled way, so that the desired excess of assembly/disassembly fluid is removed, after which plugs 2015 are inserted into the fluid outlet ports and fluid inlet port(s) is (are) also plugged allowing the remaining fluid to solidify in all the voids during a controlled cooling. According to another implementation of this principle the assembly temperature may not need to be elevated and instead of an essentially liquid (or molten) assembly/disassembly fluid, a polymeric resin freshly mixed with a hardener, and/or accelerator, and/or catalyst(s), etc. can be used. After the box and the pin are fully telescoped together, the excess of the assembly/disassembly fluid is removed, the resin remaining is allowed to polymerize, thus also forming an essentially solid seal. Many resins, including some epoxy resins can be subsequently optionally re-liquefied by heating up for optional disassemblies and pressurized at elevated temperatures for the purpose of disassembling. Glass Transition Temperature of a polymer used versus the design temperature range of a connector needs to be taken into account. Whichever implementation is used, axial and bending load cycling can be optionally used after the assemblies during the fluid solidification stage.

[0296] For all novel connectors, and in particular for those featuring lighter designs, care should be taken to make sure that the design properly addresses and prevents occurrence of buckling in all the modes buckling could potentially occur. That is in particular important during the assembly/disassembly and in operation. Buckling potential remains often unidentified during finite element analyses (FEAs), and other established engineering methods are used instead. For novel connectors one can mention for example cardioidal buckling of pin, bellows-mode buckling of pins and/or boxes, shell buckling and/or stiffener web-buckling of optional fins. Those may be caused by the assembly/disassembly fluid pressure and/or by combinations of loads under various loading scenarios.

[0297] Suitable safety measures must be applied at all times, while taking into account that considerable potential energy can be stored in the connector system during operations, during assembly and disassembly, and particularly so whenever highly compressed gas is used.

[0298] High torsional capacity arrangements can involve a single set of means limited to one connector region or any of the high torsional load capacity means can be mixed in the design of any particular connector. It is not practical to depict on drawings all the implementations of this invention involving all novel combinations of configurations feasible, accordingly FIGS. 1 through 20 should be treated as examples only, selected for the explanation of operational principles of the designs under this invention.

[0299] Newly designed connector elements should be dimensioned for specific design requirements. In particular some novel connectors require high static and fatigue torsional and bending capacities of the same order, while for example their design axial load capacities may be a great deal smaller than are those typical of the applications of the Merlin™ family connectors. In such cases novel connectors may require smaller numbers of threads similar to those shown herein as 160, 165, 350, 355, 1140, etc., and the teeth profiles used may be ‘slimmer’. The designs of such novel connectors may turn up to be more compact than are typically those used in Merlin™ family connectors used on a pipe of the same size. Stress analyses, design testing required, etc. are similar to those typically used in designing and qualifying known Merlin™ family connectors, with torsional load related considerations added. Whenever thermal loading is involved, including transients, the testing programs may need to be extended accordingly. The teeth designed to carry predominantly torsional loads or predominantly bending may have more symmetrical profiles than are those that carry axial, bending and axial pre-stressing loads, because typical loadcases of novel connectors may involve reversible torsional loads (i.e. clockwise and anticlockwise) and reversible bending loads (i.e. left and right in plane, and left and right out-of-plane) of say an adjacent elbow, while negative and positive load amplitudes are often similar.

[0300] For many novel implementations it is recommended to use a carefully selected torsional preload of interacting surfaces, which in particular can be achieved by means of radial preload which results in a desired circumferential fit between the surfaces interacting. The use of a suitable torsional preload is preferable for similar reasons as are those with regard to the axial and bending loading of traditional Merlin™ family connectors, which is obvious to anybody skilled in the art. For the same reason, whenever a close to 90° pitch angle grooving is used, or splines are used, providing such connectors with optional external ribs that would stiffen the connector in meridional bending might be considered in the design optimization. Increasing meridional bending stiffness of a connector by means of meridional ribs hardly affects its bulk torsional flexibility. For the same reason splines may be often preferred to high pitch angle threads 1120, 1121.

[0301] It is noted that the description and figures included herein do not limit the design range of the novel connectors to only those solutions depicted on drawings and/or discussed explicitly. The discussion and figures included herein characterize whole classes and families of novel connectors with only some specific representations shown as outline examples characterizing broader classes of novel connectors.

[0302] For example novel connectors utilizing fitted pins many other but shown shapes of fitted pins used in mechanical engineering (including those having for example square or hexagonal cross-sections) that are suitable for torque transfer according to this invention, can be also used to transfer torsional loads while being arranged between other box and pin surfaces, not shown on FIGS. 5, 6, 17 and 18b. For example, some designs of novel connectors may be suitable for placing fitted pin rows in the cavities of the (metal) nipple seals, like those shown as 140, at the end of a box, at the end of a pin or in both those locations, see FIGS. 12 and 13. Fitted pins can also be used between dog-clutch teeth 780, 706, 716, 990, 906, 916, etc. All such families of connectors feasible are hereby regarded as novel connectors. Connectors featuring other grooving patterns than are those shown on FIG. 11a through 11x or on other figures herein are also regarded as connectors according to this invention.

[0303] Dog-clutch teeth can also be arranged at the ends of (metal) nipple seals, like those shown as 140, again at either one or at both connector ends, see FIGS. 11n, 11p, 11r, 11w, 11x, 11y, 12 and 13.

[0304] Novel connectors can be welded to the ends of pipes to be connected, or the pins and the boxes forming a connector can be shaped in the actual pipe material used. Typically high yield strength and small grain high quality materials are used for manufacturing novel connectors. Components of novel connectors can be built from materials compatible with sweet or sour service requirements; they can be clad or lined, etc., as the design needs require. Those include boxes and/or pins and/or other components used in the same connector being made of different materials. Boxes and/or pins and or/other components used in the same connector can utilize or not utilize weld overlay(s), lining and/or cladding as required. CRAs, titanium alloys, aluminum alloys, magnesium alloys, nickel based alloys, steels and other alloys can be used depending on the design needs. Conventional or novel welding techniques, like for example friction welding and 3D printing can be used. Molding or injection molding can also be used with many metals or alloys (example aluminum alloys).

[0305] During the design multiple considerations should be taken into account, in order to provide novel connectors with high fatigue strength. In particular the accuracy of finish of the surfaces of the connector is important for pre-stressing and for high fatigue load applications. It is recommended in particular that novel connectors be built to high degree of accuracy and very smooth surface finish. It is recommended to consider carrying out shot peening, laser peening or equivalent during the manufacturing operations. High accuracy grinding and polishing should also be used, or at least considered. Benefits of thermal treatment should also be utilized where applicable, including surface thermal treatment, nitriding, etc. For small diameter connectors precision manufacturing technology should be used.

[0306] In cases of crisp separations between the axial-bending and torsional load capacity areas (for example for dog-clutch, key and spline designs) novel mechanical connectors need to be designed against accidental locking in a similar way to that, which is used in Merlin™ family connectors and/or its third party derivations, see for example U.S. Pat. No. 8,056,940.

[0307] Whenever a novel connector has to be assembled at a specific relative azimuth angle orientation of a pin versus a box, it is optionally recommended that external markings are provided to facilitate the assembly with that correct azimuth angle. An optional assembly guide system can be provided and it can be designed in varieties of ways. It can be removable, or it can be left permanently on the connector in use, etc. Subject to specific design requirements for specific connectors the above recommendations normally apply to most novel connectors.

[0308] Merlin™ family connectors and mechanical connectors of long torsional and bending fatigue life and other novel connectors have excellent leak-proof capabilities. Metal (nipple) seals at both the inside and outside diameters feature interference fits, which are very effective in sealing. For additional sealing barriers axisymmetric, zero pitch angle threads can be utilized. They are typically radially, circumferentially and axially prestressed. Non-zero pitch angle threads (wherever used) as well as external abutment surfaces such as 1459, 1659 that are interference fitted against the thread surfaces normal to the axis of the connector can also be utilized. An optional additional sealing barrier can be added by incorporating O-ring(s) elastomeric or metal, metal C-ring(s), E-ring(s), U-ring(s), etc. in the gap between inside abutment surfaces such as 1457 and/or 1657. The engineer needs to make sure that sufficient draining/exit is provided to remove the excess of the assembly/disassembly fluid after the assembly. Special means may need to be provided for that, like for example channels connecting thread tooth cavities, additional assembly/disassembly fluid outlet/inlet ports, if required etc. These may be especially required in cases where the threads utilize novel thread angle mismatching described above. In particular, it can be noted in the above context that axisymmetric threads can be utilized to provide very effective extra in-service sealing between boxes and pins of connectors according to this invention.

[0309] Wherever axisymmetric threads are utilized to provide in-service sealing, it may be beneficial to provide optional check valves or other similar arrangements in plugs closing the assembly/disassembly fluid outlet/inlet ports. Those together with optional fluid capture/removal systems can be used in a case in service swelling occurs in any sealed compartment of the annulus between the box and the pin; that can happen because of variations in the pressure of fluids transported by the connector.

[0310] In order to improve even further the leak resistance of all connectors of the types listed herein, in some applications it may be feasible to utilize for assembly and disassembly fluids that would solidify in the design range of working temperatures of the said connectors, thus becoming solid seals, or practically solid seals in cases such as using natural or synthetic resins, mastics, or mastics like substances, etc. Assembly/disassembly at elevated temperatures may be utilized for that purpose, but that need not necessarily be the case, like for example in a case of using liquid mercury or of sodium-potassium eutectic (NaK) at environmental temperatures for connectors operating in low temperatures including cryogenic temperature ranges. The fluids used can be nonorganic, organic and in particular metallic.

[0311] Care should be taken on the physical, chemical, electro-chemical, toxic and metallographic properties of the solidifying fluids used.

[0312] The physical properties include in particular the temperatures and pressures of the triple points of the fluids and their critical properties, the boiling temperatures, as well, the temperatures of recrystallization as well as the degrees of shrinkage (or otherwise) while solidifying. The chemical properties involve the fluid reactiveness with the connector materials, with the fluids transported in the pipelines or tubing as well as with other materials used. The chemical and electro-chemical properties of importance also include corrosion related aspects. Fluid toxicity can also be of importance. For example mercury cannot be used in aeronautical applications that utilize aluminum alloys. The metallographic properties include the subjectivity to diffuse into structural alloys (or other materials used), etc., (hydrogen induced brittleness, desirable or undesirable nitriding, etc.). One can also mention here phase changes in solid sealants that occur with the change of temperature, because of natural changes in crystal structures, of the solubilities of alloyed phases in other alloyed phases etc., including eutectoidal changes etc.

[0313] Ideally the fluid used would be liquid at the temperature of application and would solidify with required shrinking, if any is required at all, and remain solid in the entire range of the design conditions. The solidification shrinking, as prescribed may be beneficial, because it may partly or wholly take care of the need to remove excess assembly/disassembly fluid at the last moments of connector assembly. Such solid seals would fill all the gaps very effectively and work like O-rings. Also ideally the solid seals would have lower material strength than that of the connector material, so that they could easily deform plastically under the action of changing loads. The temperature of recrystallization would ideally fall below the design operational range of temperatures, which would enable unlimited ductility under dynamic loading (example: lead solid seals).

[0314] For applications where it could be difficult or impossible to find a fluid/solid substance meeting all the above criteria, the work below the temperatures of recrystallization may be acceptable in some applications, in particular when the solid seal material is temporarily heated above its temperature of recrystallization. Phase changes due to different phase equilibriums with temperature (like for example eutectoidal transitions) can have similar effect in lieu of recrystallization. Alloys where transitions like that take place and also other alloys should be examined thoroughly in order to make sure that no hardening like phenomena that could be unacceptable take place no undesirable phases be formed, etc. Also in some applications it may be acceptable to allow temporary melting of the sealing material in the design temperature ranges followed by re-solidification. In cases where the liquid material can boil, extreme care would be required in order to make sure that the vapors do not cause cavitation damage or other structural damage as well as that the subsequent re-solidification happens slowly enough to evenly re-distribute the seal material when it remains liquid, and not to upset the connecting functions of the connector. It is preferred to avoid boiling in the design temperature ranges. Just in case, fluid inlet and outlet plugs can be provided with pressure overload safety valves.

[0315] For applications in the environmental ranges of working temperatures sealing materials also used as primary coolant in nuclear reactors can be considered. Those include mercury, lead, lead-bismuth eutectic, sodium, potassium, sodium-potassium eutectic (NaK). Other materials include for example aluminum, aluminum alloys, copper, copper alloys including bronzes and brasses, lithium, lithium-sodium eutectic, tin, bismuth, zinc, magnesium, low melting (fusible) alloys like Rose's metal, Wood's metal, Field's metal, Darcet's alloy, safe metal, Low 117, Low 136, bend metal, Mellotte's metal, matrix metal, base metal, tru metal, cast metal, etc. Other known metals and alloys, in particular binary, ternary, etc. eutectics specially designed for particular design conditions can be also used. For example a feasibility of formations of binary lithium-potassium and ternary lithium-sodium-potassium eutectics can be investigated, and if feasible, their properties can be investigated and evaluated for use as liquid/(metal) nipple seals. Many of the above listed alloys have melting temperatures considerably below the boiling temperature of water, accordingly boiling water or water steam can be conveniently and economically used during the novel connector assemblies/disassemblies. Some remain liquid even below the water ice melting temperature.

[0316] The use of metallic or alloyed liquids/solid sealants can be of particular benefit where good heat transfer properties are required between pins and boxes. Many alloys feasible are good solders, and when applicable good solder like wetting of connector materials can be desirable both to improve solid to solid heat transfer and the sealing properties. Suitable flux substances can be added. Sealant density can be also of importance, however where the volumes of the sealant are small, the sealing and/or conduction benefits may outweigh the increase of weight of the connector.

INDUSTRIAL APPLICABILITY

[0317] Known Merlin™ family connectors are used primarily for connecting tendon and rigid riser, including Steel Catenary Riser (SCR) joints. In those applications tension and bending loads are high, while torsional loads are very small. Use of Merlin™ family connectors have been at least suggested for rigid jumper joints, however such a use would be limited to those jumper connections that do not see very high torsional loads. Novel connectors are suitable for use in rigid jumpers subject to very high static and fatigue torsional and bending loads. For example complicated three dimensional rigid jumpers are often used in ultra deepwater.

[0318] Simple shaped inverted ‘U’ or ‘M-shaped’ rigid jumpers are often used to connect subsea wellheads with Pipeline End Terminations (PLETs) or Pipeline End Manifolds (PLEMs). Those are fitted at ends of subsea pipelines that expand thermally in their longitudinal directions. PLETs and PLEMS slide on their mudmats imposing torsional loads on the vertical segments of the jumpers and connectors and bending loads on the remaining segments of those jumpers. Whenever the jumpers are short, high torsional loads must be resisted by the connectors. Novel connectors are more suitable for the use with inverted ‘U’ and ‘M-shaped’ rigid jumpers than are known Merlin™ family connectors, and they are more economical to use than collet connectors are.

[0319] Another class of examples of suitable use of novel connectors are those required for connecting elbows and pipe segments in rigid jumper designs of SCR hang-offs disclosed in U.S. Pat. No. 8,689,882 by Wajnikonis and Leverette. Those inventors state that spools resisting rotational deflections of the SCRs are subject to high torsional loads; bending loads are also mentioned.

[0320] Newer riser hang-offs according to U.S. Pat. No. 10,024,121 (Wajnikonis) ideally require novel connectors. These connectors are typically subjected to even higher static and fatigue torsional and bending loads than are those experienced in SCR hang-offs according to Wajnikonis and Leverette. In the presently discussed newer designs, the torsional and bending loads tend to be of the same order of high magnitudes.

[0321] In both the older and the newer classes of the said SCR and rigid riser hang-offs the effective tensions are very small, the actual or ‘wall’ tensions in those connectors being governed by so called ‘end cap’ pressure effects. That implies considerably lower actual or ‘wall’ tensions than are those typically experienced by known Merlin™ family connectors used for example to connect SCR joints. All the technical terms used here are used in engineering codes and are familiar to those skilled in the art.

[0322] Novel connectors can be used to connect pipes made of materials that cannot be welded together (example steel alloys and titanium alloys) or of other materials that are difficult or impossible to weld. Additional fields of industrial application may be listed. Because of their reliability and the extremely low susceptibility to leaks, novel connectors can be used for piping and pipelines in the chemical, onshore or offshore cryogenic installations and in the nuclear industry. In addition to the above features, novel connectors have very slim designs and low weights. Accordingly, they also deserve to be considered for aerospace applications, in particular cryogenic tubing or piping.

[0323] Low cost, high production volumes of connector components used in piping made of non-metallic materials, like for example plastics may be another possible field of application. Large numbers of very accurately dimensioned plastic boxes and pins used in novel connectors can be mass produced for example by casting or by injection molding. When plastic materials are used, tooling for assembling/disassembling may be low pressure hydraulic or pneumatic.