Key information

Title
APPARATUS FOR BOLTED RISER CONNECTIONS
Application number
20250725
Case type
National
Status
06.07.2026 Patent meddelt (B1)
Filed
25.06.2025
Effective date
25.06.2025
Publicly available
06.07.2026
Next annual fee due
30.06.2027
Applicant
STAVANGER ENGINEERING AS (NO)
Owner
STAVANGER ENGINEERING AS (NO)
Inventor
Tomas Johnsen (NO) et al.
Agent
LIGL IP CONSULT AS (NO)
Granted
06.07.2026
Patent number
349949
Expiry date
25.06.2045

Abstract and drawing

Disclaimer: This text has been machine-scanned and may contain errors – please refer to "Publications" for legally binding content.
A riser bolt torque tool apparatus (100) comprising: a base (10) for mounting onto a riser hang-off arrangement (13) or onto a drill floor (12); a movable arm structure (20) comprising an arm (30) extending towards riser flanges (40) supported in the riser hang-off arrangement (13); and a torque tool assembly (50) mounted at a distal arm end (30a), the torque tool assembly (50) comprising a plurality of drive mechanisms (60) for applying torque to riser bolts (42) located in the riser flanges (40), wherein the torque tool assembly (50) comprises a body structure (59) holding the plurality of drive mechanisms (60), the body structure (59) is rotatable 180 degrees between a bolt make-up orientation and a bolt release orientation, and each drive mechanism (60) comprises a drive motor (57) fixed to and rotatable with the body structure (59).

Publications

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Documents

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Date
 Date Doc. No. Process Case number In/Out Journal description To/from
 07.07.2026 07-01 Saksbehandling 20250725(349949) UT PT Registreringsbrev nasjonal patent (15) (PT20250725)
16.06.2026 06-01 Saksbehandling 20250725 UT PT Meddelelse om patent LIGL IP CONSULT AS
 08.06.2026 05-04 Saksbehandling 20250725 INN P10190NO Besvarelse av realitetsuttalelse LIGL IP CONSULT AS
 08.06.2026 05-03 Saksbehandling 20250725 INN 2026 June Revised Spec markup LIGL IP CONSULT AS
 08.06.2026 05-02 Saksbehandling 20250725 INN 2026 June Revised Spec clean LIGL IP CONSULT AS
 08.06.2026 05-01 Saksbehandling 20250725 INN Korrespondanse (Hovedbrev inn) LIGL IP CONSULT AS
 23.04.2026 04-01 Saksbehandling 20250725 UT PT Bekreftelse på fristutsettelse LIGL IP CONSULT AS
 06.11.2025 03-02 Saksbehandling 20250725 UT PT report 02:29:00
06.11.2025 03-01 Saksbehandling 20250725 UT Realitet patent LIGL IP CONSULT AS
 26.06.2025 02-01 Saksbehandling 20250725 UT Infobrev til oppfinner LIGL IP CONSULT AS
 25.06.2025 01-04 Saksbehandling 20250725 INN Patent figures LIGL IP CONSULT AS
 25.06.2025 01-03 Saksbehandling 20250725 INN Patent application LIGL IP CONSULT AS
 25.06.2025 01-02 Saksbehandling 20250725 INN Fullmakt LIGL IP CONSULT AS
 25.06.2025 01-01 Saksbehandling 20250725 INN Søknadsskjema Patent LIGL IP CONSULT AS

Description, claims and drawings

Disclaimer: This text has been machine-scanned and may contain errors – please refer to "Publications" for legally binding content. Description
3499491APPARATUS FOR BOLTED RISER CONNECTIONSThe present disclosure relates to apparatus for making up or breaking out riser connections in offshore drilling operations, in particular for spinning and/or torquing bolts in bolted riser flange connections.5BACKGROUNDIn offshore drilling and production operations, subsea risers are critical structures connecting subsea wellheads and surface platforms. These risers typically comprise multiple tubular segments connected end-to-end through flanged joints secured by 10 bolts. Each bolt is torqued to specified pre-load values to ensure structural integrity, prevent leaks, and withstand challenging offshore environmental conditions. Making up or breaking out these flanged joint connections during installation or retrieval of the riser can be challenging due to accessibility issues, space constraints, and harsh operational conditions. 15 Traditionally, bolting of subsea risers and tubular structures is done manually, which is often cumbersome, slow, and inconsistent in achieving precise torque specifications. The manual methods frequently rely heavily on operator skill and experience, leading to variations in torque application that may result in uneven bolt tensioning, thus potentially influencing joint integrity. These operations are also 20 carried out in a high-risk area, with stringent health-and-safety precautions for personnel. Such conventional methods are can therefore also slow down offshore operations, increasing operational costs and reducing efficiency.Recent developments have included various automated and semi-automated torque tools, such as clam assemblies and rotational drivers, to improve accuracy, speed, 25 and repeatability. These systems typically integrate segmented clamps with hydraulic or electric drives to position torque application devices accurately around riser tubulars. Publications which may be useful to understand the field of technology include WO 2015/038329 A1, which describes a clam assembly for connecting tubulars of a wellsite for passing fluid therethrough, having at least one 30 drive mechanism and a plurality of segments movable between open and closed positions around the tubulars, and where the drive mechanism is carried by the 3499492segments and includes a driver to drive a connector through the adjacent tubulars. Other such publications include US 10,184,850 B2, which describes a torque wrench assembly with a torque wrench head adapted to tighten and loosen a fastener; WO 2009/135201 A2, which describes a multi-bolt and nut torque wrench 5 for installing and removing bolts or nuts from flanged joints; WO 2015/093970 A1, which describes a multi-bolt or nut torque wrench device for installing or removing a plurality of threaded bolt or nut members; WO 2022/245616 A1, which describes a riser bolt torque system; WO 2022/072019 A1, which describes a robotic system for making or breaking a riser; US 6,330,918 B1, which describes an automated dog- 10 type riser make-up device and method of use; and WO 2024/220321 A2, which describes a robot end effector for spinning and torquing bolts in a riser flange.However, existing solutions still exhibit limitations in terms of, among other things, adaptability / operational flexibility, compactness, and reliability. Therefore, there remains a need for an improved riser bolt torque tool capable of reliably achieving 15 precise torque application, enhancing operational speed, safety, and consistency, while simultaneously reducing human error and operational downtime in demanding offshore environments. The present disclosure has the objective to provide such improvements, or at least useful alternatives to the state of the art. 20 SUMMARYAccording to the invention, there is provided a riser bolt torque tool apparatus comprising: a base configured for mounting onto a riser hang-off arrangement or onto a drill floor adjacent the riser hang-off arrangement; a movable arm structure supported on the base; the movable arm structure comprising an extendable arm 25 configured to, in use, extend towards riser flanges supported in the riser hang-off arrangement; and a torque tool assembly mounted at a distal end of the extendable arm, the torque tool assembly comprising a plurality of drive mechanisms configured for applying torque to riser bolts located in the riser flanges, wherein the torque tool assembly comprises a body structure configured to hold the plurality of drive 30 mechanisms, the body structure is rotatable 180 degrees about a horizontal axis between a bolt make-up orientation and a bolt release orientation, and each drive 3499493mechanism comprises a drive motor fixed to the body structure and rotatable with the body structure.The detailed description and appended claims below outline further inventive examples and embodiments.5BRIEF DESCRIPTION OF THE DRAWINGSThe invention will now be explained in greater detail with reference to the accompanying drawings, in which:Fig.1 illustrates a riser bolt torque tool apparatus in a typical use situation, showing 10 the apparatus mounted on a riser hang-off arrangement and engaging a riser flange.Fig.2 illustrates the riser bolt torque tool apparatus in closer detail, highlighting the extendable arm and torque tool assembly.Fig.3 is a top view of the riser bolt torque tool apparatus, showing the arrangement of a movable arm structure and torque tool assembly. 15 Fig.4 is a cut view along the vertical plane A-A of Fig.3, illustrating vertical and horizontal extendability of the arm structure and the positioning of the torque tool assembly.Fig.5 shows the torque tool assembly in a retracted orientation, pivoted upwardly and away from a riser during hoisting or lowering operations. 20 Fig.6 illustrates a side view of a riser bolt torque tool apparatus having a compliant interface between the extendable arm and the torque tool assembly.Fig.7 is a cut view along the vertical plane B-B of Fig.6, detailing an elastic joint and its capability to permit limited angular deflection.Figs.8-10 illustrate various configurations of a torque tool assembly, showing the 25 arrangement of drive mechanisms and pivotable carriers.Figs.11-12 show a body structure of a torque tool assembly in different orientations, illustrating the make-up and release positions of drive mechanisms. 3499494DETAILED DESCRIPTIONThe present disclosure relates to a riser bolt torque tool apparatus 100. Fig.1 illustrates the apparatus 100 in a typical use situation and Fig.2 illustrates the 5 apparatus 100 in closer detail. A riser 41 is suspended from a hoisting system on a drilling rig, which may be part of a mobile offshore drilling unit (MODU). A riser hangoff arrangement 13 is provided at a drill floor 12 of the rig, and operable to support a part of the riser 41 extending downwardly towards a subsea wellhead. The riser hang-off arrangement 13 may be a spider/gimbal arrangement having support 10 members (such as movable dogs) operable to engage a flange 40 of the riser 41 and carry the weight of the riser 41 being suspended into the sea below. A new section of riser 41 can be provided for connection with the part of the riser 41 suspended from the riser hang-off arrangement to build the riser 41, or sections of riser 41 may be successively removed if retrieving the riser 41. The riser flanges 40 15 forming the riser flange connection may be connected via a plurality of bolts 42, which must be made up or broken out accordingly.According to an example, the apparatus 100 has a base 10 configured for mounting onto the riser hang-off arrangement 13 (such as on a so-called spider deck or otherwise to the spider/gimbal arrangement), or onto the drill floor 12 adjacent the 20 riser hang-off arrangement 13. By mounting the base 10 on the riser hang-off arrangement 13, the apparatus 100 may move with the riser 41, which may have some movement due to movement of the MODU in the sea. Alternatively, the base 10 of the apparatus 100 may be mounted on the drill floor 12, and any movement of the riser 41 may be compensated for by the apparatus 100 itself. 25 The apparatus 100 has a movable arm structure 20 which is supported on the base 10. The movable arm structure 20 comprises an extendable arm 30 configured to, in use, extend inwardly towards the riser flanges 40 being supported in the riser hangoff arrangement 13.A torque tool assembly 50 is positioned at a (relative to the base 10) distal end 30a 30 of the extendable arm 30. The torque tool assembly 50, examples of which are described in further details below, comprises a plurality of drive mechanisms 60 3499495distributed on a body structure of the torque tool assembly 50 and configured for applying torque to the riser bolts 42. In use, the torque tool assembly 50 can engage several of the bolts 42 simultaneously by operating the movable arm structure 20 to lower the torque tool assembly 50 onto the bolts 42. 5 In this example, the movable arm structure 20 is vertically extendable from the base 10. This functionality may be provided by a height adjustment actuator, in this example a hydraulic cylinder 11.Fig.3 illustrates a top view of the apparatus 100 and Fig.4 illustrates a cut view along the vertical plane A-A of Fig.3. The arm structure 20 may, for example, have 10 a vertical guide column 27 (Fig.4) which is received in a corresponding receptacle or sleeve in the base 10 for permitting vertical movement of the arm structure 20. Also visible in Fig.4, the extendable arm 30 may be horizontally extendable by means of an arm adjustment actuator, in this example a hydraulic cylinder 15. The extendable arm 30 may, for example, be arranged as a telescopic arm for this 15 purpose. Alternatively, the extendable arm 30 may be formed by articulated joints.In the illustrated example, the movable arm structure 20 is vertically extendable from the base 10 by an upright arrangement, and the extendable arm 30 is extendable by a horizontal arrangement which is parallel to the drill floor 12. This need, however, not be the case, and vertical and/or horizontal motion can alternatively be provided 20 by for example slanting arrangement of the relevant components. The extendable arm 30 may, for example, be arranged with an angle relative to the drill floor 12. Optionally, the movable arm structure 20 and/or the extendable arm 30 may comprise a plurality of movable arm parts connected by articulated (flexible) joint(s), for example similarly as described in the abovementioned WO 2024/220321 A2. 25 The torque tool assembly 50 may be pivotable relative to the extendable arm 30 about a vertical axis and the movable arm structure 20 may be pivotable relative to the base 10 about a vertical axis. With reference to Figs 3 and 4, the movable arm structure 20 may for example mounted on a rotatable guide column 27 that is journalled in the base 10 for rotation about a first vertical axis x. A pivot joint 29 30 between the arm 30 and the torque tool assembly 50 provides rotation about a second vertical axis y, spaced from the first axis x. The pivoting or rotational position 3499496of the movable arm structure 20 relative to the base 10, and of the torque tool assembly 50 relative to the extendable arm 30, may be controlled by appropriate actuators. The two spaced vertical pivots allow the arm 30 to extend towards the riser 41 at a non-radial angle (as compared to the radial direction of the riser 41), 5 and to pivot the torque tool assembly 50 towards the riser 41. This permits adjustment of the torque tool assembly 50 relative to a given position of the bolts 42, which can vary according to the motions of the riser 41. The torque-tool assembly 50 can in such a case be swung into correct alignment with the riser flanges 40 even when the arm 30 does not point directly (radially) toward the centre line of the riser 10 41.In other examples, illustrated in Figs 4 and 5, the torque tool assembly 50 may be pivotable relative to the extendable arm 30 about a horizontal axis so as to flip the torque tool assembly 50 upwardly and away from the riser 41. This may, for example, be used when hoisting or lowering the riser 41. Optionally, this may be 15 combined with a full retraction of the extendable arm 30, as illustrated in Fig.5, so as to move the torque tool assembly 50 farther away from the riser 41 during hoisting or lowering operations.For example, the torque tool assembly 50 may be mounted to the distal end 30a of the extendable arm 30 by a hinge or trunnion bracket 35 that defines a horizontal 20 pivot axis. The pivot axis may be substantially perpendicular to a horizontal longitudinal axis of the arm 30, and lies generally parallel to the drill floor plane. This arrangement lets the torque tool assembly 50, which normally occupies a substantially horizontal operational orientation (Figs 1-4) when in engagement with the riser flange 41, be flipped upwardly and outwardly to a retracted orientation (Fig. 25 5). In the retracted orientation, the torque tool assembly 50 thus provides better access for running the riser 41 and other deck operations. The hinge bracket 35 is preferably sized to allow a pivot sweep of at least 45°, more preferably at least 60°, and in one embodiment about or at least 75° from the operational orientation. A detent or latch may be provided to lock the assembly in either orientation. An 30 actuator 39 can be coupled between the extendable arm 30 and the torque tool assembly 50 to power the flipping motion. 3499497While the hydraulic cylinder 11, the hydraulic cylinder 15 and the actuator 39 have been illustrated here as hydraulic piston-cylinder arrangements, other actuation mechanisms can equally well be used, such as linear electric actuators, ball screw actuators, or other types. 5 In other examples, illustrated in Figs 6 and 7, a compliant interface is provided between the extendable arm 30 and the torque tool assembly 50. Fig.7 illustrates a cut view along the vertical plane B-B of Fig.6. As shown schematically at reference numeral 55, an elastic joint is disposed at the assembly interface 56. The elastic joint 55 may take the form of an elastomeric bushing, a leaf-spring or feather-pack 10 arrangement, or any other resilient coupling capable of resilient bending capability.The elastic joint 55 permits the torque tool assembly 50 to pivotably yield relative to the extendable arm 30 in the event of forces acting on the torque tool assembly 50. This may, for example, be the case if there is movement of the riser 41 (due to MODU sea motion) when the torque tool assembly 50 is engaged with the bolts 42. 15 Providing limited, resilient bending capability in the elastic joint 55 can reduce mechanical loads on the riser bolt torque tool apparatus 100. In one implementation, the elastic joint 55 allows angular deflection of up to about ±5° to ±10°. The elastic joint 55 may permit deflection in any direction, such as in a horizontal plane, in a vertical plane, or in both horizontal and vertical planes. Mechanical end stops can be 20 incorporated to limit travel/deflection beyond the desired range.Optionally, the compliant interface / elastic joint 55 can be incorporated with the functionality of the pivot joint 29 and/or the hinge bracket 35, whereby these components in such a case can be designed to permit limited resilient bending capability. 25 In other examples, the riser bolt torque tool apparatus 100 can be provided with a free‑float functionality, in which the apparatus 100 can be switched into a free‑float (follow) mode so that the torque tool assembly 50 rests on the engaged riser bolts 42 and passively follows any relative motion between the base 10 and the riser 41. The free-float functionality may include vertical float and/or horizontal float. 30 For example, the height adjustment actuator, illustrated as a hydraulic cylinder 11 acting between the base 10 and the movable arm structure 20, can be provided with 3499498a two‑position float valve. In an active configuration, the valve separates the cylinder chambers so that the actuator supports the weight of the arm structure 20 and enables powered raising or lowering. In a float configuration, the chambers are interconnected, equalising pressure and allowing the piston rod to slide freely. The 5 movable arm structure 20 may therefore move up or down on the guide column 27 under external forces while the torque tool assembly 50 remains seated on the bolts 42.Particularly, vertical free-float operation may be used during make-up of the flange connection. Once the torque tool assembly 50 has been brought into engagement 10 with the flange bolts 42, the operator may select a vertical free‑float mode. For example, in the scenario illustrated in Fig.1, the torque tool assembly 50 has been positioned around the riser 41 and above the riser bolts 42 in the active mode / operational configuration. (The terms mode and operational configuration is used interchangeably herein.) The torque tool assembly 50 may then be lowered onto the 15 bolts 42, and the height adjustment actuator (here, the hydraulic cylinder 11) put in float mode by switching the float valve. The weight of the torque tool assembly 50 is then at least partially carried by the bolts 42. Because the actuator is in float mode, the movable arm structure 20 can move downward automatically as the bolts 42 are threadably advanced during the make‑up cycle. No active positional control is 20 required, and the drive mechanisms 60 can apply torque while the movable arm structure 20 simply follows the motion of the bolts 42. When the target torque is achieved, the float valve is re‑closed, returning the actuator to its load‑holding and active mode for subsequent disengagement and retraction. Advantageously, using free-float operation as opposed to active vertical position control during make-up 25 reduces the risk of overloading individual bolts 42 vertically, for example when spinning the bolts 42 out of storage threads in the upper flange 40 of the flange connection.The method may comprise bringing the torque tool assembly 50 into contact with the riser bolts 42 prior to switching the height-adjustment actuator 11 from the active 30 load-holding operational configuration into the free-float operational configuration, i.e. to operate the movable arm structure 20 to actively bring the torque tool assembly 50 into direct contact with the bolts 42 before switching to free-float mode. Alternatively, switching the height-adjustment actuator 11 into the free-float 3499499operational configuration can be done after positioning the torque tool assembly 50 directly above the plurality of riser bolts 42 but without actively bringing the torque tool assembly 50 into contact with the riser bolts 42. In this manner, switching to vertical free-float mode will let the torque tool assembly 50 move downwardly and 5 engage the bolts 42 by means of gravity.Advantageously, during make-up the method may comprise operating the heightadjustment actuator 11 continuously in free-float mode to first spin the riser bolts 42 out of storage threads in an upper flange part of the bolted riser flange connection, and then to thread the bolts 42 into make-up threads in a lower flange part of the 10 bolted riser flange connection to make up the connection. Conventionally, when building the riser 41, a new riser section may be provided with the riser bolts 42 arranged in such storage threads in the lower flange 40 of the new riser section being brought to the riser hang-off arrangement 13. (The lower flange 40 of the new riser section then becomes the upper flange part of the riser flange connection when 15 it is made up, as is visible in Fig.1.) With the height‑adjustment actuator 11 kept continuously in free‑float mode, the drive mechanisms 60 are then first operated to spin the bolts 42 out of the storage threads of the now‑upper flangepart. Immediately thereafter the same float mode allows the movable arm structure 20 and torque tool assembly 50 to follow the subsequent threading‑in of the bolts 42 20 into the deeper make‑up threads of the confronting lower flange part, completing the flange connection without having to re‑set positional control of the movable arm structure 20 and torque tool assembly 50. Risk of damage to the bolts 42 during such mechanical handling of the bolts 42 in this process can be mitigated by operating the movable arm structure 20 and torque tool assembly 50 continuously in 25 float mode.In horizontal float, an arm‑adjustment actuator, illustrated as hydraulic cylinder 15, is equipped with an analogous float valve. When switched to float mode, the cylinder 15 permits un‑pressurised extension or retraction so that the extendable arm 30 can be pushed or pulled laterally by riser movements without inducing side‑loads. In the 30 example illustrated in Figs 3 and 4, corresponding functionality can be implemented in any actuators operable to pivot the movable arm structure 20 relative to the base 10 about the first vertical axis x and to pivot the torque tool assembly 50 relative to the extendable arm 30 about the second vertical axis y, as described above. 34994910Re‑engaging the powered mode can be accomplished by resealing the float valves, after which the cylinders can resume normal positional control.In any of the vertical free-float or horizontal free-float configurations, the apparatus 100 may include flow‑restrictive elements that limit actuator velocity and thus 5 prevent shock loading. For vertical float, the float valve (or a dedicated throttle or orifice insert) may for example be sized so that hydraulic flow between the opposing chambers of the height‑adjustment actuator 11 is limited; the movable arm structure 20 can therefore descend only at a controlled rate. Consequently the torque tool assembly 50 can settle more gently onto the bolts 42 instead of dropping abruptly, 10 avoiding impact damage and minimising spindle‑end load spikes. An analogous restrictor can be provided in the horizontal float circuit to damp lateral motion.Figs 8-12 illustrate further examples of torque tool assemblies 50, some of which or aspects thereof are also visible in Figs 1-7. The torque tool assemblies 50 may be used with any of the riser bolt torque tool apparatus 100 examples described or 15 claimed herein, or with other apparatuses. Other suitable apparatuses may be various types of robotic arms or articulated-robot manipulators, such as six-axis robots with serial articulated joints, operable to carry and handle the torque tool assembly 50 at a drill floor 12 or a riser hang-off arrangement 13. The torque tool assembly 50 can be coupled via an interface 56′ to any such lifting or positioning 20 apparatus 100 capable of positioning the assembly 50 at or adjacent a riser flange 40 held in the riser hang-off arrangement 13. The assembly 50 carries a plurality of independently driven drive mechanisms 60 that deliver make-up or break-out torque to respective riser bolts 42 disposed in the flange(s) 40 on a suspended riser 41. In the illustrated examples, the assembly 50 comprises first and second segments 25 52, 54 that are selectively movable (via hinges 64) between an open configuration, in which the segments 52,54 spread apart to clear the riser 41, and a closed configuration, in which the segments 52,54 substantially encircle the riser 41 and locate the drive mechanisms 60 directly adjacent corresponding bolts 42. The two segments 52,54 may be pivotally joined to one another at a hinge mechanism 64. 30 Alternatively, as in the illustrated examples here, each segment 52,54 may be hinged to a central, intermediate tool part 53 that also has the interface 56′ to the 34994911carrier apparatus 100. The segments 52,54 and (optionally) the intermediate part 53 together form a body structure 59 that supports the individual drive mechanisms 60. In the illustrated arrangement, drive mechanisms 60 can be mounted not only on the two movable segments 52,54 but also on the intermediate part 53, thereby reducing 5 the complexity of the movable segments 52,54 and easing positioning of the assembly 50 at the riser flange(s) 40. An optional elastic joint 55 (for example, an elastomeric bushing or stacked spring pack), as described above, can be provided at the interface 56’.Alternatively, the assembly 50 may be provided without movable segments 52,54, 10 for example comprising only the intermediate part 53 as illustrated in Figs 8-10. In such an example, two apparatuses 100 which each has a respective assembly 50 may be used to make up or break out riser bolts 42, for example in the manner illustrated in the abovementioned WO 2024/220321 A2 or WO 2022/072019 A1. The example in Figs 8-10 illustrate an assembly 50 for an 8-bolt riser flange 40, whereby 15 in such an example of two apparatuses 100, each apparatus 100 could handle four bolts 42 with the four drive mechanisms 60 arranged on the intermediate part 53, which makes up the body structure 59, and the movable segments 52,54 as shown in Figs 8-10 would be absent.Illustrated in Figs 8-10, each drive mechanism 60 may be mounted on a carrier 49 at 20 the body structure 59. The carrier 49 is, in turn, movably mounted on the body structure 59, in the illustrated example pivotably mounted about a vertical pivot axis. In this manner, the drive mechanism 60 can be swung inward or outward before final engagement with the bolt 42. The carriers 49 may be arranged with two drive mechanisms 60 arranged thereon, whereby the two drive mechanisms 60 share a 25 common pivot bracket. These configurations can enhance the operational flexibility of the assembly 50, for example simplifying use of the assembly 50 with flanges 40 having a non-symmetric bolt arrangement.Figs 11 and 12 illustrate another example. In Figs 11 and 12, only parts of the assembly 50 are shown, and in this example the assembly 50 is configured for a 6- 30 bolt riser flange 40, similarly as illustrated in Figs 1-7. The examples in Figs 1-7, 11 and 12 may, however, equally well be configured for a different number of flange bolts than six. (Such as eight.) Conversely, the example illustrated in Figs 8-10 may 34994912equally well be configured for a different number of flange bolts than eight. (Such as six.) The features described in relation to Figs 11 and 12 are applicable to any of the examples or embodiments described above or elsewhere herein.Illustrated in Figs 11 and 12, the body structure 59 may hold the drive mechanisms 5 60. Each of the drive mechanisms 60 has a drive motor 57 arranged at (for example integral with) the body structure 59, and a wrench socket 58 to engage a respective bolt 42. The body structure 59 may be mounted for 180-degree rotation about a horizontal axis. The body structure 59 can thus be “flipped” in the horizontal plane between a bolt make-up orientation (with sockets 58 of the drive mechanisms 60 10 facing downward to tighten) and a bolt release orientation (with the sockets 58 still facing downward, but with the body structure 59 and drive motors 57 inverted so the drive direction of the drive motors 57 is reversed). Fig.11 illustrates the body structure 59 in the make-up orientation, while Fig.12 illustrates the body structure 59 flipped 180 degrees and in the bolt release orientation. In this manner, the same 15 assembly 50 can be used for both bolt make-up and bolt release, without the need for the drive motors 57 to be bi-directional. This simplifies the design of the assembly 50, or avoids the need to have different assemblies 50 for the different operations.The wrench sockets 58 may be selectively detachable from the drive motors 57 20 through releasable torque-transmission members 61 (which, for example, may comprise an engagement face 62, such as a splined bar or hex stem, to cooperate with the drive motor 57 to transfer torque to the wrench sockets 58). Each drive motor 57 may include a through-bore or opposed receptacle so that the transmission member 61 can be inserted from either side of the body structure 59. 25 In the illustrated example, the transmission member 61 is inserted from one side (from above in the illustrated orientation) and releasably connectable to the wrench socket 58 located at the opposite side of the body structure 59. As such, the drive mechanisms 60 can be released and turned around when the body structure 59 is “flipped”. Fig.12 illustrates the drive mechanisms 60 in the process of being turned 30 after flipping the body structure 59, such that the wrench sockets 58 face downwards. A lock pin 63 can, for example be used to secure the wrench socket 58 to the transmission member 61 in this example. 34994913In another option, the socket 58 and transmission member 61 are permanently coupled and inserted as a unit from the required side; in yet another each drive motor 57 may carry a continuous drive rod that projects above and below the body structure 59, allowing the socket 58 to be released from, and remounted on, that rod 5 at either end. A further variant provides permanently mounted sockets 58 on both sides, enabling a simple half-turn of the body structure 59 to place the desired set of sockets 58 into service.In one example, each drive mechanism 60 may comprise a selectively detachable spinner motor 65 which is mountable in operative connection to a respective wrench 10 socket 58 both in the bolt make-up orientation and bolt release orientation of the body structure 59. The spinner motor 65 may, as in the illustrated example, be integral with a transmission member 61 insertable into a receptacle or through-bore of the drive motor 57. Alternatively, the spinner motor 65 may be mountable on the body structure 59 such that it is in operative engagement with the socket 58. For 15 example, if the drive mechanism 60 has a continuous drive rod projecting at either side of the body structure 59 or permanently mounted sockets 58 on both sides (as described above), the spinner motor 65 may be releasably mountable at the (at any time) upward-facing side of the body structure 59 and in engagement with the drive rod or upward-facing socket. 20 The spinner motor 65 may be bi-directional and, for example, hydraulically or electrically driven. The spinner motor 65 may be used to spin riser bolts 42 into or out of storage threads or main threads of the flange(s) 40, before (or after) the drive motor 57 applies make-up or release torque.Alternatively, a spinner motor man be integral with the drive motor 57 and/or 25 permanently arranged in or at the body structure 59.As described above in relation to Figs 1-7, when preparing for operation, the supporting apparatus 100 positions the body structure 59 directly adjacent the flange 50, and optionally closes the segments 52,54 (if present) around the riser 41. When the sockets 58 are aligned with their respective bolts 42, the drive motors 57 30 can be energised to apply torque on the bolts 42, either drawing the flanges 40 together or releasing them. 34994914The invention is not limited by the embodiments described above; reference should be had to the appended claims.
Claims
34994915CLAIMS1. A riser bolt torque tool apparatus (100) comprising:a base (10) configured for mounting onto a riser hang-off arrangement (13) or onto a drill floor (12) adjacent the riser hang-off5 arrangement (13);a movable arm structure (20) supported on the base (10);the movable arm structure (20) comprising an extendable arm (30) configured to, in use, extend towards riser flanges (40) supported in the riser hang-off arrangement (13); and10 a torque tool assembly (50) mounted at a distal end (30a) of the extendable arm (30), the torque tool assembly (50) comprising a plurality of drive mechanisms (60) configured for applying torque to riser bolts (42) located in the riser flanges (40),wherein the torque tool assembly (50) comprises a body structure15 (59) configured to hold the plurality of drive mechanisms (60) and each drive mechanism (60) comprises a drive motor (57) fixed to the body structure (59), characterised in thatthe body structure (59) is rotatable 180 degrees about a horizontal axis between a bolt make-up orientation and a bolt release orientation, and20 each drive mechanism (60) is rotatable with the body structure (59).2. The riser bolt torque tool apparatus (100) according to claim 1, wherein each drive mechanism (60) comprises a selectively detachable wrench socket (58) which is mountable in downward-facing orientation both in the bolt make-up25 orientation and bolt release orientation of the body structure (59).3. The riser bolt torque tool apparatus (100) according to any preceding claim, wherein each drive mechanism (60) comprises a selectively detachable spinner motor (65) which is mountable in operative connection to a30 respective wrench socket (58) both in the bolt make-up orientation and bolt release orientation of the body structure (59).349949164. The riser bolt torque tool apparatus (100) according to claim 3, wherein the spinner motor (65) is mountable on either of a first and second side of the body structure (59) and operatively connected to a wrench socket (58) located at an opposite, second or first side of the body structure (59).55. The riser bolt torque tool apparatus (100) according to any preceding claim, wherein each drive mechanism (60) comprises a releasable torquetransmission member (61) having an engagement face (62) for connection to the drive motor (57).106. The riser bolt torque tool apparatus (100) according to claim 5, wherein the drive motor (57) comprises a receptacle for the torque-transmission member (61) at opposite sides of the body structure (59).15 7. The riser bolt torque tool apparatus (100) according to claim 6, wherein the receptacle extends through the drive motor (57) and the torque-transmission member (61) is insertable through the drive motor (57) from either of a first and second side of the body structure (59) and releasably connectable to a wrench socket (58) located at an opposite, second or first side of the body20 structure (59).8. The riser bolt torque tool apparatus (100) according to any preceding claim, wherein the movable arm structure (20) is vertically movable relative to the base (10) by means of a height adjustment actuator, and the height25 adjustment actuator has (i) an active operational configuration in which the height adjustment actuator is active to hold the weight of the movable arm structure (20), and (ii) a free-float operational configuration in which the height adjustment actuator allows un‑powered vertical movement.3034994917PATENTKRAV1. Anordning (100) for momentpåføring på stigerørsbolter, omfattende:en base (10) konfigurert for montering på en stigerørsopphengsanordning (13) eller på et boredekk (12) ved siden av stigerørsopphengsanordningen (13), 5 en bevegelig armstruktur (20) understøttet av basen (10),hvor den bevegelige armstrukturen (20) omfatter en forlengbar arm (30) som, under bruk, er innrettet til å strekke seg mot stigerørsflenser (40) som er understøttet i stigerørsopphengsanordningen (13), ogen momentverktøyenhet (50) montert ved en ende (30a) av den uttrekkbare 10 armen (30), hvor momentverktøyenheten (50) omfatter en flerhet drivmekanismer (60) innrettet til å påføre moment på stigerørsbolter (42) anordnet i stigerørsflensene (40),hvor momentverktøyenheten (50) omfatter en kroppsstruktur (59) innrettet til å bære den nevnte flerheten av drivmekanismer (60), og hver drivmekanisme 15 (60) omfatter en drivmotor (57) fastgjort til kroppsstrukturen (59), karakterisert ved atkroppsstrukturen (59) er dreibar 180 grader om en horisontal akse mellom en orientering for tiltrekking av bolter og en orientering for løsning av bolter, og hver drivmekanisme (60) er dreibar sammen med kroppsstrukturen (59). 202. Anordning (100) for momentpåføring på stigerørsbolter ifølge krav 1, hvor hver drivmekanisme (60) omfatter en selektivt avtakbar pipenøkkel (58) som kan monteres i en nedovervendt orientering både i orienteringen for tiltrekking av bolter og i orienteringen for løsning av bolter til kroppsstrukturen (59).253. Anordning (100) for momentpåføring på stigerørsbolter ifølge et hvilket som helst av de foregående krav, hvor hver drivmekanisme (60) omfatter en selektivt avtakbar spinnmotor (65) som kan monteres i operativ forbindelse med en respektiv pipenøkkel (58) både i orienteringen for tiltrekking av bolter og i 30 orienteringen for løsning av bolter til kroppsstrukturen (59).4. Anordning (100) for momentpåføring på stigerørsbolter ifølge krav 3, hvor spinnmotoren (65) kan monteres på enten en første eller en andre side av34994918kroppsstrukturen (59), og er operativt forbundet med en pipenøkkel (58) som er anordnet på en motsatt, andre eller første side av kroppsstrukturen (59).5. Anordning (100) for momentpåføring på stigerørsbolter ifølge et hvilket som5 helst av de foregående krav, hvor hver drivmekanisme (60) omfatter et frigjørbart momentoverføringselement (61) med en inngrepsflate (62) for forbindelse med drivmotoren (57).6. Anordning (100) for momentpåføring på stigerørsbolter ifølge krav 5, hvor10 drivmotoren (57) omfatter et mottak for momentoverføringselementet (61) på motsatte sider av kroppsstrukturen (59).7. Anordning (100) for momentpåføring på stigerørsbolter ifølge krav 6, hvor mottaket strekker seg gjennom drivmotoren (57), og15 momentoverføringselementet (61) kan innføres gjennom drivmotoren (57) fra enten en første eller en andre side av kroppsstrukturen (59) og kan frigjørbart forbindes med en pipenøkkel (58) anordnet på en motsatt, andre eller første side av kroppsstrukturen (59).20 8. Anordning (100) for momentpåføring på stigerørsbolter ifølge et hvilket som helst av de foregående krav, hvor den bevegelige armstrukturen (20) er vertikalt bevegelig i forhold til basen (10) ved hjelp av en høydejusteringsaktuator, og hvor høydejusteringsaktuatoren har: (i) en aktiv driftskonfigurasjon der høydejusteringsaktuatoren er aktiv for å bære vekten av den bevegelige25 armstrukturen (20), og (ii) en friflyt-driftskonfigurasjon der høydejusteringsaktuatoren tillater vertikal bevegelse uten aktiv kraftpåføring.
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Patent classes

IPC classesE21B 17/08E21B 19/16CPC classesE21B 17/085E21B 19/16

Citations

WO 2015/038329 A1 (A1)WO 2024/220321 A2 (A2)US 10184850 B2 (B2)WO 2022/072019 A1 (A1)WO 2009/135201 A2 (A2)

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Owners
STAVANGER ENGINEERING AS
Moseidveien 1 4033 STAVANGER NO (STAVANGER Municipality, Rogaland county)Org. number: 921003862Inventors
Tomas Johnsen
Bergljots gt. 16 4041 HAFRSFJORD NO (STAVANGER Municipality, Rogaland county)
Lukasz Bigos
Litlabergarmen 28 4051 SOLA NO (SOLA Municipality, Rogaland county)

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LIGL IP CONSULT AS
LIGL IP CONSULT AS

Org. number: 922948836

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Org. number: 922948836
Reference: P10190NO

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