A torque device for oil field use and method of operation for same

[0001] The present invention relates to a torque device for use in oil fields, and its mode of operation. More specifically, the present invention relates to a torque device for use in an oil field, and a method thereof, wherein the torque device includes a first torque device member that has an operational axis of rotation, and the first torque actuator is rotatably connected to the first member torque devices at a first radial distance from the axial line of the first member of the torque device. The invention also relates to a method of operating a torque device for use in oil fields.

[0002] In this document, which is associated with fittings for land and sea oil fields, the word pipe is used to describe generally understood elongated elements. Depending on the operation in question, the elongated element may be a cylindrical or non-cylindrical tool or any related object that is associated with the tool connector.

BACKGROUND OF THE INVENTION [0003] A typical powered torque device used to create or separate pipe connections in oil extraction applications includes a pair of torque device members, herein referred to as "first torque device member" and "second torque device member", but often referred to as 'feed ticks' and 'support ticks'. In operation, the feed pliers rotate the first pipe relative to the second pipe, while the support pliers keep the second pipe relatively stationary. Each of these ticks has a socket for placing the appropriate pipe. Typically, each of these forceps has a set of clamps that typically include clamp jaws for grasping the pipe when the pipe is placed in the tick seat. An example can be found in WO 92/18743, which is also considered the closest prior art.

[0004] In some powered torque devices, the torque applied by the feed pliers to the first tube is from a pair of double-sided hydraulic cylinders. Powered torque devices typically impose significant shear loads on the pipe connection as a result of current push / pull forces due to imbalance of hydraulic cylinders and the eccentricity of the support and supply forceps caused by clamp forceps. These shear loads can contribute to incorrect pipe connections. In these powered torque devices, lateral loads on pipe threads can change the friction force in the pipe connection and cause some masking of the torque. The term "torque masking" refers to everything that causes the torque read from the powered torque device to deviate from the actual torque experienced by the pipe connection.

[0005] In some powered torque devices, mechanical guides are used between the booster and feed tongs to provide a common axis of rotation for the tubes of booster ticks and feed ticks when rotating the feed ticks. The guides are usually in the form of a guide ring system concentric to the theoretical axis of the pipe and positioned between the support and supplying forceps and / or between the supplying forceps and the external structure. The current state of the art system typically operates during the application of torque when both the support and feed tongs are clamped on the pipes and during no rotation when the feed clamps are not clamped on the pipe. In these powered torque devices, the centric deviation between the supply and support pliers can cause masking of the torque. In particular, when the centric deviation is greater than the clearance of the guide rings, some of the clamping force will be transferred to the surface of the guide rings. The friction generated by turning the power ticks will act as a drum brake, leading to the fact that the visible torque will be greater than the actual torque.

[0006] Errors in the reading of the torque can make it difficult to accurately make pipe connections, especially in applications where pipe connections are to be made with a torque within a narrow torque range.

[0007] The object of the invention is to remove or reduce at least one of the disadvantages of the prior art.

[0008] This object is achieved according to the invention by the advantages of the features disclosed in the following description and in the appended claims.

Brief Description of the Invention [0009] According to a first aspect of the invention, there is provided a torque device for use in an oil field comprising a first torque device member that has an operational axis of rotation, and wherein the first torque actuator is rotatably connected to the first torque device member at a first radial distance from the axial line of the first member of the torque device, wherein the rod or second member of the torque device is rotatably connected to the first member of the torque device in a second radius of the distance extending in the opposite direction to the first radial distance from the axial line, and wherein the rod, alternatively the second member of the torque device is rotatably connected to the other part of the cylinder bracket, and where the cylinder bracket is movable radially with respect to the working axis, but its rotation in a plane that is perpendicular to the axis of work is limited.

[0010] The suspension of the torque device allows the first member of the torque device to move freely in a plane perpendicular to the axis of operation.

[0011] When it is attached to a pipe that is mounted radially, the working axis coincides with the longitudinal axis of the pipe. The first member of the torque device rotates with the pipe. If the torque device is equipped with a first torque actuator and rod,

The actuator support can, when the first member of the torque device rotates with the pipe, move in the direction to or from the working axis. PZ / 2939 / JDN EP 2 753 785 B1

[0012] If the torque device has a first torque actuator and a second torque actuator, where one extends and the other compresses, with equal speed and when rotating the first member of the torque device, the actuator bracket may be substantially stationary. Any discrepancy in speed between the two torque cylinders causes the cylinder bracket to move toward or away from the operating axis.

[0013] The cylinders may be of any useful form, such as hydraulic, pneumatic and electric cylinders.

[0014] The first torque actuator and rod, alternatively the second torque actuator, may in the first part corresponding to the second part of the actuator bracket, be rotatably connected to the actuator bracket about the axis of the bracket that connects the first part to the second part.

[0015] Although only slight movements of the first member of the torque device are envisaged along the operating axis, the torque actuator and rod can freely tilt around the axis of the bracket that connects the first part to the second part.

[0016] The first member of the torque device may be connected to the second member of the torque device having a common operating axis. The first member of the torque device may be power ticks, while the second member of the torque device may be supportive ticks.

[0017] The actuator bracket may be connected to the second member of the torque device.

[0018] The actuator bracket may be pivotally connected to a second member of the torque device about a rotation axis which has a direction allowing the actuator bracket to rotate toward or away from the operating axis.

[0019] The two members of the torque device may thus work as a pair when the second member of the torque device forms a base for the actuator bracket and thus for the first member of the torque device.

[0020] The first torque actuator may be connected to the body of the torque device member of the first torque device member through a clamp of the first actuator.

[0021] The rod, alternatively the second torque actuator, may be connected to the body of the torque device member of the first torque device member via a clamp of the second actuator.

[0022] The length of the cylinder clamp must be adapted to the length of the cylinders and to the distance between the first and second parts of the cylinder bracket.

[0023] The first part and the second part of the cylinder support can be placed at the same height in the direction of the working axis.

[0024] The first torque actuator may, at least within a certain operating range, be parallel to the rod, alternatively to the second torque actuator.

[0025] According to a second aspect of the present invention, there is provided a method of operating a torque device for use in an oil field that includes a first torque device member that has an operational axis of rotation and wherein the first torque actuator is pivotally connected to the first torque device member at a first radial distance from the axial line of the first member of the torque device in which the method includes as follows:

- connecting the rod or second torque actuator to the first member of the torque device at a second radial distance that extends in the opposite direction to the first radial distance from the axial line;

- a rotatable connection of the first torque actuator to the first part of the actuator bracket;

- a rotatable connection of the rod, alternatively a second torque actuator, to the second part of the actuator support; and

- allowing radial movement of the actuator bracket relative to the operating axis, but limiting the rotation of the actuator bracket in a plane that is perpendicular to the working axis.

[0026] The method may further comprise rotatable connections of the first torque actuator in the first portion of the actuator bracket and the rod, alternatively the second torque actuator, to the second portion of the actuator bracket about the axis of the bracket that connects the first part with the second part.

[0027] The method may further comprise connecting the first member of the torque device to the second member of the torque device which has a common operating axis.

[0028] The method may further comprise connecting the actuator bracket to the second member of the torque device.

[0029] The method may further include a rotatable connection of the actuator bracket to a second member of the torque device about a rotation axis which has a direction that allows the actuator bracket to rotate in a direction toward and away from the operating axis.

[0030] The method may further include placing the first portion and the second portion of the actuator bracket at the same height relative to the operating axis.

[0031] The device and method of the present invention allow the first tube to be rotated without introducing lateral forces. Transverse forces introduced by prior art tools due to their stationary transverse connection tend to create additional forces

Thread friction, masking or interfering with the torque reading of the tool connector connection. PZ / 2939 / JDN EP 2 753 785 B1

Brief description of the figures [0032] An example of a preferred device and method is explained below with reference to the attached drawings, where:

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is a perspective view of the torque device of the present invention;

shows section II of Fig. 1;

shows section II-II in Fig. 2;

is a perspective view of a torque device of another embodiment;

shows a side view of the support pad;

is a perspective view of the torque device of Fig. 4 where other degrees of freedom are indicated;

shows the hydraulic control circuit of the torque device;

shows the control circuit of Fig. 7 in the normal rotation mode;

shows the control circuit of Fig. 7 in high rotation mode;

shows a side view of the torque device;

shows the same as Fig. 1, but with the first torque device member removed and the torque actuators removed;

is a perspective view from the bottom side of the first member of the torque device;

shows section XX of Fig. 10.

shows the same as Fig. 13, but with the terminal bodies activated;

shows the same as Fig. 13, but with the first torque device member at a different rotation angle;

is a perspective view of the first clamp body with a flexible jaw grip; is a cross-sectional view of the flexible jaw grip system in another embodiment; is a perspective view of the jaw grip;

is a cross-sectional view of the jaw holder of Fig. 18 of the jaw holder system in yet another embodiment;

shows the clamp jaw in a displaced arrangement relative to the first pipe;

is a sketch of the first pipe in various positions relative to the first member of the torque device;

presents a graph of the proportions of individual caliper body travels;

shows a simplified speed regulation diagram;

presents a sketch of resultant pipe positions in the first member of the clamp device resulting from passive compensation;

presents a larger-scale perspective view of the caliper arrangement;

PZ / 2939 / JDN EP 2 753 785 B1

Fig. 26 is the same as Fig. 2, but with the terminal bodies in the active connected position;

Fig. 27 is a graph where the change in torque is plotted relative to the rotation angle of the torque device;

Fig. 28 shows details of the first and second pipes;

Fig. 29 is a schematic drawing of the tool searching for a tool connector;

Fig. 30 is a graph in which the positions of the tip are plotted relative to the axial distance;

Fig. 31 is a schematic drawing of a tool that searches for a tool connector of another embodiment;

Fig. 32 is a schematic drawing of the tool searching the tool connector of yet another embodiment; and

Fig. 33 is a block diagram related to a measuring system.

Detailed description of the invention [0033] It should be noted that the figures, in order to better reveal the features of the invention, usually only show the features necessary for disclosure. This means that many of the necessary components, such as fasteners, power sources, control cables and devices, are not shown. However, these elements and their effects are known to the skilled person.

[0034] In the figures, reference number 1 denotes a powered torque device used to create or separate connections of tool joints 2 between the first pipe 4 and the second pipe 6. The torque device 1, see Fig. 1, comprises a first torque device 10 which has a body of a torque device member 12.

[0035] The body of the torque device member 12 in this embodiment comprises an upper part 14 and a lower part 16, both parts 14, 16 having U-shaped seats 18 for receiving the first pipe 4. The upper and lower parts 14, 16 are spaced apart from each other and connected through the side parts 20. The upper and lower refer to the operating position of the torque device 1.

[0036] The first member of the torque device 10 has three terminal bodies 22, 24, 26, which are designed to move between a retracted, passive position, where the terminal bodies 22, 24, 26 are detached from the first pipe 4, and the active, extended the position where the terminal bodies 22, 24, 26 are in contact with the first pipe 4. Of these terminal bodies 22, 24, 26, the first terminal body 22 includes a terminal arm extension 27 that is suspended on the first terminal shaft 28, see Fig. 2, the second terminal body 24 includes a terminal arm extension 29 which is suspended on the second shaft clamp 30, and the third clamp body 26 is linearly movable in the guide 32, see Fig. 3. The stems of clamps 28, 30 are in this embodiment attached to the body of the torque device member 12.

[0037] The XYZ coordinate system is shown in Fig. 1. The Z axis is orthogonal to the XY plane. The torque device 1 has an operational axis of rotation 34, which extends in the Z direction. The operating axis 34 usually coincides with the axial line of the first tube 4 when the torque device 1 is clamped on the first tube 4.

[0038] The body of the first member of the torque device 12, which is supported by a non-shown structure, can be substantially free to slide or slide slidably in the XY plane.

[0039] Looking from the opposite side to the U-shaped socket 18, see Fig. 2, the body of the first clamp 22 is located on the left side of the working axis 34, the body of the second clamp 24 is located on the right side of the working axis 34, and the body of the third terminal 26 is located between the bodies of the first and second terminals 22, 24. The bodies of the terminals 22, 24, 26 are here displaceable within the body of the torque device member 12 in a plane parallel to the XY plane.

[0040] The bodies of the first, second and third clamps 22, 24, 26 are connected and moved by means of the first clamp cylinder 36, the second clamp cylinder 38 and the third clamp cylinder 40 respectively. The clamp cylinders 36, 38, 40 are attached to the side part 20 the body of the member of the torque device 12 and are connected to their respective terminal bodies 22, 24, 26 by means of intermediate struts 43.

[0041] The first torque actuator 42 is rotatably connected to the first member of the torque device 10 by a clamp of the first actuator 44 at a first radial distance 46 from the axial line 48 of the first member of the torque device 10. When the first member of the torque device 10 is in the middle position, Axial line 48 is parallel to the X direction. The rod 50 is rotatably connected to the first member of the torque device 10 by a clamp of the second actuator 52 at a second radial distance 54 from the axial line 48. The first and second radial distance 46, 54 are on opposite sides to the axial line 48. The connections of the first torque actuator 42 and the rod 50, respectively, the clamp of the first actuator 44 and the clamp of the second actuator 52, can be in the form of ball joints, which are often used in actuators.

[0042] The first actuator 42 is also pivotally connected to the first portion 56 of the actuator bracket 58, while the rod 50 is pivotally connected to the second portion 60 of the actuator bracket 58. The first and second parts 56, 60 of the actuator bracket 58 form a fork.

[0043] As shown in Fig. 2, there is a variable clearance 62 between the third clamp cylinder 40 and the cylinder bracket 58.

[0044] The actuator bracket 58 is movable in the X direction, which is in a radial direction relative to the operating axis 34 of the first member of the torque device 10. However, the rotation of the actuator bracket 58 in the XY plane perpendicular to the operating axis 34 is limited.

[0045] Fig. 1 shows an actuator bracket 58 movable in a guide member 64 that is attached to a structure not shown.

[0046] During normal operation, the axial line 48 is perpendicular to the working axis 34. Due to the possible imperfect position of the clamped first tube 4 relative to the first member of the torque device 10, the working axis 34 may or may not coincide with the axial line 48.

[0047] When the torque is to be applied to the first pipe 4, the first pipe 4 is placed in the U-shaped socket 18 of the first member of the torque device 10. The terminal bodies 22, 24, 26 are moved by the respective terminal cylinders 36, 38, 40 to their active positions by engaging the first pipe 4. Because the first torque device member 10 before clamping to the first tube 4, in addition to connecting to the first torque actuator 42 and rod 50, can move freely in the XY plane, the first member of the torque device 10 when the terminals bodies 22, 24, 26 will cover the first pipe 4, it will position itself on the first pipe 4 so that the axial line of the first pipe 4 becomes the operating axis 34 of the torque device 1.

[0048] In the embodiment shown in Fig. 1, the second pipe 6 is attached to the not shown structure at least in a direction perpendicular to the working axis 34. When the first actuator 42 extends or compresses, the torque is set on the first pipe 4 around the working axis 34. The actuator bracket 58 is moved through the rod 50 in the X direction, which is in the radial direction relative to the operating axis 34, setting the torque on the first tube 4, without introducing radial forces in the first tube 4 in the XY plane.

[0049] In an alternative embodiment, the rod 50 may be replaced with a second torque actuator 66, as shown in Fig. 4.

[0050] As shown in Fig. 4, the torque device 1 includes a first member of the torque device 10 and a second member of the torque device 68, which is located below the first member of the torque device 10.

[0051] The second member of the torque device 68 is similar in construction to the first member of the torque device 10 and includes a body of the torque device member 70 with an upper portion 72.

[0052] The Yoka yoke 74 extends in the X axis direction from the second member of the torque device 68 and below the actuator bracket 58. The actuator bracket 58 is connected to the Yoka yoke 74 via a rotary bearing 76 which rotates about a rotation axis 77 which is parallel to the Y direction. The actuator bracket 58 can rotate freely in the rotary bearing 76 to move in a radial direction to and from the first member of the torque device 10, see Fig. 10 and 11, wherein the first member of the torque device 10 and the torque cylinders 42, 66 are not visible.

[0053] In the embodiment shown in Fig. 4, the first portion 56 and second portion 60 of the actuator bracket 58 are rotatably connected to the actuator bracket 58 and can rotate about the axis of the bracket 78 that extends between the first and second parts 56, 60. The axis of the bracket 78 is parallel to the direction Y. The first and second parts 56, 60 can thus rotate freely about the axis of the bracket 78 when the actuator bracket 58 rotates on the rotary bearing 76. The first and second parts 56, 60 may alternatively be made as a cardan joint or articulation not shown here.

[0054] If the torque device 1 is to be used for making tool joints 2, see Figs. 1 and 4, the second member of the torque device 68 is clamped on the second pipe 6 and the first member the torque device 10 is clamped on the first pipe 4. If the first actuator 42 stretches at the same rate as the second torque actuator 66 compresses, the actuator bracket 58 remains stationary while transmitting the torque to the tool connector 2. Any discrepancy in speed between the two torque actuators 42, 66 will cause the actuator bracket to move 58 in the guide member 64 around the pivot bearing 76 and pivot axis 77, respectively. In this way, the actuator bracket 58 is movable to prevent radial forces being applied to the pipes 4, 6, allowing only torque to be applied to the pipes 4, 6.

[0055] Fig. 5 shows the support washer 80 that aims to allow the upper first member of the torque device 10 to slide relative to the lower second member of the torque device 68, as well as to allow the first and second members of the torque device 10, 68 traveling the physical distance towards each other when the pipes 4, 6 are screwed together with the angle of rotation of the upper member of the first torque device 10.

[0056] The support pad 80 includes an upper layer 82 and a lower layer 84. The upper layer 82 can be laminated to the lower layer 84 by suitable means, including gluing. The bracket pad 80 may be disc shaped. The upper layer 82 is a layer that is in contact with the first member of the torque device 10. The top layer 82 is made of a low-friction, wear-resistant material, which allows the first member of the torque device 10 to slide freely relative to the second member of the torque device 68. The lower layer 84 is a layer that is in contact with the upper part 72 of the second body torque device member 70.

[0057] The lower layer 84 is made of a compressible, elastic material that allows a small degree of compression without permanent deformation to maintain relative movement along the operating axis 34 between the first member of the torque device 10 and the second member of the torque device 68. The material of the bottom layer 84 is pressed against the second member of the torque device 68 under the weight of the first member of the torque device 10 and by traveling a physical distance through the first member of the torque device 10, which is not shown when it is rotated by a rotation angle to make a tool joint connection 2. The compressibility of the material of the lower layer 84 is selected so as to keep the first torque device member 10 sufficiently above the second torque device member 68 and to ensure sufficient movement of the first torque device member 10 along the operating axis 34 when making the tool joint connection 2, thus preventing other contact between the first member of the torque device 10 and the second member of the torque device 68.

[0058] Possible movements of the first member of the torque device 10 are shown in Fig. 6. The arrow indicates the rotational position 86 of the first member of the torque device 10 around the operating axis 34, the arrows show the possible movement of the first member 88 torque devices 10 in the XY plane, the arrows show the possible movement of the actuator bracket 90 of the actuator bracket 58 about the axis of rotation 77. The arrows show the rotational movements of 92 torque cylinders 42, 66 in respective connections.

[0059] The torque device 1 can be controlled by the power supply circuit 100, as shown in Fig. 7 [0060] The first torque actuator 42, shown in Fig. 7, has a first positive chamber 102 and a first negative chamber 104. A second torque cylinder Rotary 66 has a second positive chamber 106 and a second negative chamber 108.

[0061] When the hydraulic fluid is supplied to the positive chambers 102, 106, the respective torque cylinders 42, 66 stretch and compress when the hydraulic fluid is supplied to the negative chambers 104, 108.

[0062] Hydraulic fluid under pressure is normally supplied to the pump port P (port P) of the directional valve 110, and the hydraulic fluid is drained from the directional valve 110 through the drainage port T (port T). The first positive line 112 connects the forming port M (port M) on the directional valve 110 with the first positive chamber 102 and with the first closed valve 114. The second positive line 116 connects the distribution port B (port B) of the directional valve 110 to the positive chamber 106 and to the second closed valve 118. The first negative line 120 connects the first negative chamber 104 to the third closed valve 122 and to the second closed valve 118. The second negative line 124 connects a second negative chamber 108 with first and third closable valves 114, 122.

[0063] The torque device 1 has two modes of operation: normal mode and high torque mode. When the tool connector 2 is made in normal mode, see Fig. 8, the directional valve 110 is activated so that the hydraulic fluid under pressure flows through port M and through the first positive line 112 to the first positive chamber 102 of the first torque actuator 42. The first closed valve 114 is closed. When the first torque actuator 42 extends, fluid in the first negative chamber 104 flows through the first negative line 120, the third closed valve 122 and the second negative line 124 to the second negative chamber 108. The second closed valve 118 is closed.

[0064] Flow from the first negative chamber 104 to the second negative chamber 108 causes the second torque actuator 66 to stretch. When the second torque actuator 66 extends, fluid from the second positive chamber 106 flows through the second positive line 116 to port B and then to port T of directional valve 110.

[0065] In one embodiment, see Fig. 7, port P of the directional valve pump 110 is connected to the pressure control valve 126.

[0066] When the tool connector 2 is made in high torque mode, see Fig. 9, the directional valve 110 is activated so that hydraulic fluid under pressure flows through port M and through the first positive line 112 to the first positive chamber 102 of the first torque actuator 42. The first closed valve 114 is closed. When the first torque actuator 42 stretches, the fluid in the first negative chamber 104 flows through the first negative line 120, the second closed valve 118 and the second positive line 116 to port B, and then to port T of directional valve 110. The first and third closed valve 114 and 122 are closed. No fluid can flow from the second negative chamber 108. The extension of the second torque actuator 66 is therefore prevented.

[0067] When the normal and high torque modes separate the tool connector 2, they are similar to those described above forming the tool connectors. Such operations can also be used for idle return of torque cylinders 42, 66. Table 1 shows the valve positions in different modes of operation.

[0068] As explained above, the first torque device 10 can slide freely in the XY plane, while the actuator bracket 58 can, to a limited extent represented by reference number 90 in Fig. 6, move freely around the axis of the rotary bearing 76. At least part of this movement is in the direction of the X axis, which is in the radial direction relative to the working axis 34.

[0069] To explain the difference in torque between the normal mode and the high torque mode, the operation of making the tool joint 2 was selected. The first and second ray lengths 46, 54, see Fig. 1, have equal lengths L. Then with a certain fluid pressure to the first positive chamber 102, the force exerted in the direction of expansion of the first torque actuator 42 is equal to F.

[0070] In normal operation mode, when the first torque actuator 42 extends, fluid flows from the first negative chamber 104 of the first torque actuator 42 and to the second negative chamber 108 of the compressive second torque actuator 66. The forces in both torque cylinders 42, 66 are equal, but operate in opposite directions to keep the cylinder support 58 stationary, which is freely movable towards and from the first torque cylinder 42. Forces from the two torque cylinders 42, 66 form a few forces. The hydraulic pressure is divided into two torque cylinders 42, 66. Each of the resulting forces that are equal but operate in opposite directions is equal to f.

[0071] The resulting force in the first torque cylinder 42 is equal to Ff. Because both torque cylinders 43, 66 have equal dimensions; the force in the first torque cylinder 42 decreases by the same amount that is transferred to the second torque cylinder 66. Thus, Ff = f, the force acting on each torque cylinder 42, 66 in normal mode is half the force acting in the first actuator torque 42 in high torque mode.

[0072] In normal creation mode, the torque exerted on the first tube 4 is the sum of the forces from the first torque actuator 42 (f = 0.5F) multiplied by the first radial distance 46 (L) and force from the second torque actuator 66 (f = 0.5F) multiplied by the second radial distance 54 (L).

0.5F * L + 0.5F * L = FL [0073] In high torque generation mode, the first negative chamber 102 is discharged to port T. The force from the first torque actuator 42 is equal to F. The movement of the second torque actuator 66 is limited and the reaction force is also equal to F. The sum of the moments acting on the first pipe 4 in high torque mode is therefore equal to:

F * L + F * L = 2FL [0074] At the same hydraulic fluid pressure, the torque in high torque mode is twice as high as in normal mode.

[0075] The operational "bandwidth" of the torque device 1 is increased by using the control circuit 100.

[0076] Limiting the stretching of the second torque actuator 66 when creating with high torque, will move the bracket of the actuator 58 a distance when operating at high torque.

Table 1

<td>Powered function torque device rotary</td><td>Torque Mode rotary</td><td>Valve 110</td><td>Valve 114</td><td>Valve 118</td><td>Valve 122</td>

<td>creation</td><td>normal</td><td>creation</td><td>closed</td><td>closed</td><td>open</td>

<td>separation</td><td>normal</td><td>separation</td><td>closed</td><td>closed</td><td>open</td>

<td>creation</td><td>tall</td><td>creation</td><td>closed</td><td>open</td><td>closed</td>

<td>separation</td><td>tall</td><td>separation</td><td>open</td><td>closed</td><td>closed</td>

[0077] Torque device 1 is equipped with a guide system 130 for aligning the first member of the torque device 10 with a second member of the torque device 68, Fig. 10. The guide system 130 includes a guide ring 132 that is attached to one of the first or second of the torque device 10, 68. The guide ring 132 is here divided into the first guide ring portion 134, the second guide ring portion 136 and the third guide ring portion 138, Fig. 11. The three guide ring parts 134, 136, 138 are located on and attached to the top portion 72 of the second device member torque 68.

[0078] The guide system 130 further includes a first guide element 140, a second guide element 142 and a third guide element 144, which are movably connected in succession to the first or

PZ / 2939 / JDN EP 2 753 785 B1 2, 10, 68, in this case with the first member 10, and move with its first terminal body 22, second terminal body 24 and third terminal body 26 respectively. , see Fig. 12. The third guiding element 144 extends through the longitudinal slot 146, in the lower part 16 of the body of the torque device member 12.

[0079] In Fig. 13, the terminal bodies 22, 24, 26 are located in their retracted positions. The first, second and third guide elements 140, 142, 144, which move in their respective terminal bodies 22, 24, 26 are similar to the first guide ring segment 134, the second guide ring segment 136 and the third guide ring segment 138 respectively. The guide elements 140, 142, 144 do not hide enough to simultaneously contact the corresponding guide ring sections 134, 136, 138. Only two of these guide elements 140, 142, 144 are in contact with their guide ring sections 134, 136, 138, at any time, to avoid excessive frictional force arising between the guide elements 140, 142, 144 and the corresponding guide ring sections 134, 136, 138. The axis of rotation, not shown, will be approximately in the center of the guide ring 132.

[0080] In Fig. 14, the clamp bodies 22, 24, 26 are placed in their active positions by clamping on the first pipe 4. In this position, the guide elements 140, 142, 144 are offset from the guide ring segments 134, 136, 138. It is impossible for a friction force to arise in the guide system 130 when the terminal bodies 22, 24, 26 are clamped and aligned along the working axis 34.

[0081] When the terminal bodies 22, 24, 26 are in the retracted position, the guide system 130 guides the first and second members of the torque device 10, 68 relative to each other during the return movement of the first and second torque actuators 42, 66 when the rotational position 86 of the first member of the torque device 10 is changed, see Fig. 15.

[0082] It should be noted that the support washers 80, as well as the first, second and third segment of the guide ring 134, 136, 138, as shown in Figs. 13, 14 and 15 are attached to the second member of the torque device 68, see Fig. 11, and are not attached to the first member of the torque device 10, which is shown in Figs. 13, 14 and 15.

[0083] Since the first member of the torque device 10 is free to slide in the XY plane, the guide system 130 ensures that the first member of the torque device 10 is approximately aligned with the second member of the torque device 68 when the first member of the torque device 10 does not is pinned to the first pipe 4. Nevertheless, the guide system 130 is not activated when the terminal bodies 22, 24, 26 of the first member of the torque device 10 are in the extended active position.

[0084] A flexible jaw holder 150 is shown in Fig. 16. The clamp jaw 152 is axially, i.e. generally in the Z direction, slidably positioned in the clamp holder 154. The connection on

Dovetail 156 is often used to hold the clamp jaw 152 in the clamp holder 154. The clamp holder 154 is part of the first clamp body 22. Other clamp bodies 24, 26 can be designed in the same way .

[0085] In Fig. 16, a jaw holder 158 is shown in the form of a body having a first surface 160 that rests against the jaw of a clamp 152 on its rear surface 162. A flexible body 164 in the form of a band which is disposed in a groove 166 in the jaw holder 158 presses the jaw grip 158 towards the jaw of the clamp 152. A second surface 168 prevents the jaw of the clamp 158 from moving. The jaw holder 158 may also be on the opposite end portion of the jaw 152.

[0086] In Fig. 17, the jaw grip 158 is shown in another embodiment in which the jaw grips 158 are located at each end of the jaw of the clamp 152. The jaw grips 158 are here made of a resilient material such as rubber or polyurethane. In Fig. 17, jaw grippers 158 are located between the clamp body 22 and the clamp jaw 152.

[0087] In another embodiment, see Figures 18, 19, the jaw holder 158 is in the form of a formed elastic plate. A portion of the groove 170 is disposed between the first fold portion 172 and the second fold portion 174.

[0088] As shown in Fig. 19, the first fold portion 172 adheres to the rear surface 162 of the clamp jaw 152, and the second fold portion 174 adheres to the housing 176 of the clamp body 22, as well as to the clamp holder 154.

[0089] The jaw grip 158, as shown in Fig. 19, is functional in itself, but a flexible body 164 can be arranged in the groove portion 170 to better secure the position of the jaw grip 158.

[0090] A not shown stop can be provided to limit movement of the clamp jaw 152 in the clamp holder 154.

[0091] When the force moves the jaw of the clamp 152 in the clamp holder 154, as shown in Fig. 16, the flexible body 164 is slightly stretched. When this force is removed, the flexible body 164 returns the jaw of the clamp 152 to its original position.

[0092] Similarly, when the jaw of the clamp 152 is moved a distance of 178, see Fig. 17, the material of the jaw holder 158 is compressed. When the clamp jaw 152 is unloaded, it returns to its original position due to the expansion of the jaw grip 158.

[0093] When a similar movement takes place in the embodiment shown in Fig. 19, the jaw holder 158 is bent, as indicated by dashed lines. When the clamp jaw 152 is unloaded, it returns to its original position due to the elastic action of the jaw grip 158 and the flexible body 164.

[0094] In Fig. 20, the jaw of the clamp 152 is shown in a connected position offset from the first pipe 4, causing displacement 180 between the axial line 182 of the jaw of the chuck 152 and the operating axis 34 of the first pipe 4.

[0095] Fig. 21 is a sketch of a system in which the first clamp body 22 with its extended clamping arm 27 is hinged around the first clamping mandrel 28, as shown in Fig. 2. The first pipe 4 is shown in three different dimensions as a larger pipe diameter 186, medium diameter pipe 188 and smaller diameter pipe 190.

[0096] During the clamping operation, the first clamp body 22 and the second clamp body 24, see Fig. 2, moves away from opposite sides of the first pipe 4 at equal speeds. The first pipe 4 is thus centered on the axis line 48 regardless of its diameter during crimping. The terminal bodies 22, 24, 26 include clamp jaws 152. The positions of the first terminal body 22 shown in Fig. 21 also apply to the second terminal body 24.

[0097] When the position of the first clamping plunger 28 in this embodiment is stationary relative to the first member of the torque device 10, the axial line 182 of the clamping jaw 152 intersects the axial line of the larger pipe 192 in the tangential position of the larger pipe 194, the axial line of the medium pipe 196 in the tangential position the average pipe 198 and the axial line of the smaller pipe 200 at a tangential position of the smaller pipe 202.

[0098] The axial lines 192, 198, 200, which are different, correspond respectively to the operating axis 34 of the larger diameter pipe 186, the average diameter pipe 188 and the smaller diameter pipe 190.

[0099] The third clamp body 24, see Fig. 2, includes a larger diameter pipe 186 at the contact position of the larger pipe 204, an average diameter pipe 188 at the contact position of the medium pipe 206 and a smaller pipe 190 at the contact position of the smaller pipe 208.

[0100] The distances I, II that the first and second clamp body 22, 24 must travel to align the individual pipes 186, 188, 190 are different from the distance III that the third clamp body 26 must travel. The relationship between equal distances I, II and distance III is not linear. However, using first order approximation as shown in Fig. 22, the shift distance 180 is significantly reduced; say ten times compared to an uncompensated system.

[0101] In Fig. 22, the displacement distance III of the third clamp body 26 is on the abscissa axis, and the respective displacement distances I, II of the first and second clamp body 22, 24 are set along the ordinate axes. Line 210 shows the relationship between displacement distances I, II, relative to displacement distance III. The speed of movement of the first and second body of the clamp 22, 24 is adjusted so that they travel the first and second displacement distance I, II between the tangential position of the larger pipe 194 and the tangential position of the smaller pipe 202 at the same time as the third body of the clamp 26 travels the third distance III between the contact position of the larger pipe 204 and the contact position of the smaller pipe 208.

[0102] Because the speed of movement of the terminal bodies 22, 24, 26 in one embodiment is constant; the retracted positions of individual terminal bodies 22, 24, 26 are on line 210

PZ / 2939 / JDN in the first and second retracted positions 212 and third retracted positions 214, respectively. Positions 212 and 214 are also indicated in Fig. 21.

[0103] Fig. 23 shows a basic hydraulic unit that allows different clamping speeds to be obtained. The first, second and third terminal actuators 33, 38, 40, here in the form of a hydraulic cylinder, see Fig. 2, are respectively connected to the first flow control valve 216, the second flow control valve 218 and the third flow control valve 220. Flow control valves 216 , 218, 220 are designed to operate within the differential pressure range. Within this range, the flow is kept around the set point. The flow control valves 216, 218 are calibrated to the same flow value, and the third flow control valve 220 is calibrated to a lower flow rate than the first and second flow control valves 216, 218. The ratio between the flow to the third cylinder 40 and the flow in the first and second cylinders 36, 34 is determined by the geometry of the clamping mechanism and given by the slope and shape of the line 210, see Fig. 22. After valves 216, 218, 220 are adjusted once, do not require frequent adjustment.

[0104] As explained above, the third clamp body 26 must begin in the third retracted position 214, which is closer to the first pipe 4 compared to the first and second clamp body 22, 24, which are in the first and second retracted positions 212.

[0105] Flow valves 216, 218, 220 are supplied with hydraulic fluid through the supply line 222, which receives fluid through the reduction valve 224. The clamping sequence ends when no flow is detected through the reduction valve 224. The pressure set on the reduction valve 224 and present downstream of the flow control valves 216, 218, 220 is equal to the required clamping force.

[0106] This allows detecting when the flow is still passing through the pressure reducing valve 224 and thus monitoring whether the clamping has ended or not. The first tube 4 will also be secured when positioned in the center relative to the first member of the torque device 10, since the terminal bodies 22, 24, 26 will continue to move until they all come into contact with the first tube 4. The set pressure must be above the minimum value that will ensure that the flow valves 216, 218, 220 are within the operating range; otherwise, terminal bodies 22, 24, 26 may move at unexpected speeds.

[0107] Fig. 24 shows the result of passive compensation of the center of the pipe using differential clamp movement speeds. The position of the axial line of the larger pipe 192 is further from the bottom 226 of the shaped socket 18, see also Figures 1 and 2 than the axial line of the average pipe 196. Therefore, it is not necessary to remove the same amount of material from the bottom 226 of the U-shaped socket 18, because the axial line of the larger pipe 192 should be in the same position as the axial line of the medium pipe 196. Line 228 points to the bottom of the U-shaped socket 18 of the uncompensated system .

[0108] The system applies to both the first member of the torque device 10 and the second member of the torque device 68.

[0109] Fig. 25 shows the adjustable arrangement of terminal pins. In this embodiment, the first clamping plunger 28, which has a clamping plunger axis 230, is coupled to the body of the first member of the torque device 12 by means of slewing bearings 232, here in the form of disks. Bearings 232 have bearing axes 234 that are eccentric to the axis of the caliper stem 230.

[0110] In one embodiment, the first clamp plunger 28 has a lock 236 that includes the locking plunger 238. The locking plunger 238 can be positioned in any of a plurality of lock apertures 240 in the body of the first member of the torque device 12.

[0111] By turning the caliper plunger 28 together with bearings 232 in the body of the first member of the torque device 12, the position of the body of the first caliper 22 relative to the first member of the torque device 10 can be adjusted, see Fig. 26.

[0112] In Fig. 26, a first pipe 4 with a diameter corresponding to the diameter of the smaller pipe 190 of Figures 21 and 24 is placed in the first member of the torque device 10.

[0113] The axial line 182 of the clamp jaw 152 in the body of the second clamp 24 has a displacement distance 180 relative to the axial line of the smaller pipe 200 that corresponds to the operating axis 34.

[0114] By turning the first terminal plunger 28 by an angle 242, as shown on the left of Fig. 26, the axial line 182 of the clamp 152 in the body of the first clamp 22 is coaxial with the center 200 of the smaller diameter pipe 190.

[0115] Arrow 244 indicates the current relative position of the first terminal plunger 28.

[0116] The system applies to both the first member of the torque device 10 and the second member of the torque device 68.

[0117] In one embodiment shown in Fig. 6, the first torque actuator 42 is equipped with a first position sensor 250, which is designed to provide a signal that reflects the position of movement of the first torque actuator 42. The second torque actuator 66 is equipped with a second position sensor 252. The actuator bracket 58 has an actuator bracket position sensor 254.

[0118] In one embodiment, the position sensor 255 may be contactless relative to the first member of the torque device 10.

[0119] The first torque actuator 42 has a first force sensor 256 which is designed to provide a signal that reflects the force exerted by the first torque actuator 42. In an embodiment in which the first torque actuator is electrically driven, the first force sensor 256 can be located in the first portion 56 of the actuator bracket 58; alternatively it can measure power. In an embodiment in which the first torque actuator 42 is fluid driven, the first force sensor 256 may be in the form of a fluid pressure sensor. It is then possible to calculate the strength.

[0120] Similarly, the second torque actuator 66 has a second force sensor 258.

[0121] In one embodiment, the torque can be measured using a third force sensor 259 located in the actuator bracket 58.

[0122] Sensors 250, 252, 254, 255, 256, 256, 258 and 259 may be of any suitable construction as known to the person skilled in the art.

[0123] Sensors 250, 252, 254, 256, 256, 258 and 259 are connected to the torque control system 260 via wires 262.

[0124] The torque control system 260 is programmed to calculate the torque or torque-data. Torque data is determined by comparing the torque value with the actual rotation position of the first member of the torque device (10). It is therefore possible to relate the actual torque transmitted to the first tube 4 through the first member of the torque device 10 to the actual rotation position 86 of the first member of the torque device 10.

[0125] In one embodiment, the torque control system 260 is equipped with a memory 264 for storing at least said information.

[0126] When the first member of the torque device 10 changes its rotational position 86, see Fig. 15, the length of the torque arm 266 between the operating axis 34 and the axial line of the first and second actuator 42, 66 changes. When the first member of the torque device rotates 10, the length of the torque arm 266 varies approximately sinusoidally, as indicated by curve 268 in Fig. 27. In Fig. 27 the abscissa axis represents the rotational position 86 of the first member of the torque device 10 and the ordinates represent the uncompensated torque in percent. Torque reduction is usually in the range of 7% to a rotational position variation of 86 ± 30 degrees.

[0127] This change in torque arm 266 can be compensated by a change in torque actuator force.

[0128] In the case of fluid driving the first and second torque actuators 42, 66, the fluid pressure may be regulated. An adjustable pressure control valve 126 of the control system 100 for the first and second torque actuators 42, 66 is shown in Fig. 7.

[0129] In an embodiment in which the first and second torque actuators 42, 66 are electric, the current and / or voltage consumption may be varied according to a change in torque arm length 266 to maintain a constant torque of the first torque device member 10 or according to the set torque-rotation curve.

[0130] A typical socket 270 of the tool connector 2 is shown in Fig. 28. The socket 270, which during normal use is located in the upper part of the second tube 6, has a cylindrical surface 272 with a diameter of 0t with the so-called "hard band" 274 near the bead connection walls 276. The first tube 4 includes a plug 278 at its lower end. Socket 270 and plug 278 together form a tool connector 2. Socket 270 has a tool connector socket arm 280, and plug 278

PZ / 2939 / JDN EP 2 753 785 B1 has a tool connector arm 282. When creating a tool connector, 2 arms 280, 282 are adjacent.

[0131] When the socket 270 is in the form of a tube, it is exposed to deformations originating from the terminal bodies 22, 24, 26, in particular if it is gripped close to the socket of the tool connector socket 280 of the socket 270, see Fig. 26. Such deformation may mask the reading torque when creating and separating the tool joint 2.

[0132] The second pipe 6 has a pipe diameter of 0p, while the overall length from arm to arm is G. Socket 270 has a thickening of the connection from the distance of the arm of the tool socket A to the distance of the cylindrical face B. In addition, socket 270 has a base with a hard band 274 to the distance of the tool connector socket arm C and top with a hard band 274 to the distance of the tool connector socket arm D.

[0133] The hard band 274 has the form of a protruding ring which is made of relatively strong material. The clamp jaws 152 of the torque device 1 should not grip the hard band 274 because the clamp jaws 152 may be damaged in this way. The jaws of the clamp 152 should preferably grip the seat 270 as close as possible to the hard band 274 and as far away from the seat of the tool connector 280 as possible to avoid or reduce the abovementioned deformations. The jaw of the chuck 152 is shown in Fig. 20.

[0134] Fig. 29 shows the device, in this case referred to as the Tool Joint Finder - TJF (tool connector finder) 290 for reading the relative position of the pipe surface 4, 6. TJF 290 includes a sensor tip 292 which is connected to a linear sensor 294 behind using the 296 guide in the form of a measuring rod. The signal from the linear sensor 294 is transmitted via a wire 298 to the measurement control system 300, which is programmed to at least convert the signal from the linear sensor 294 into the readable graph 302 shown in Fig. 30.

[0135] In Fig. 30, which shows the measured profile of the socket 270 of Fig. 28, the abscissa represents the position of the sensor tip 292, and the axial distance of the socket 270 is plotted along the ordinates. The contour of the hard band 274 is clearly visible on curve 302.

[0136] The sensor tip 292 in one embodiment is pressed against the first tube 6 by means of a tip actuator 304, here in the form of a fluid-powered plunger. The tip actuator 304 can in one embodiment be connected to the measuring tip 222 by means of the tip spring 306, as shown in Fig. 31. After actuating the TJF 290, the tip actuator 304 moves the tip spring 306 to a predetermined position or a position determined by a sensor linear 294. The radial movement of the sensor tip 292 relative to the socket 270 during the measuring operation is received by the spring of the tip 306.

[0137] In one embodiment, as shown in Fig. 32, the actuator of the tip 304 presses against the seat 270 of the first pipe 4 preferably with a constant force. If the external force is greater than the force from the tip cylinder 304, the tip cylinder 304 will subside.

[0138] In Fig. 32, the sensor tip 292 is shown connected to the actuator of the tip 304 by a hinge 308 that allows the sensor tip 292 to locally move backwards and forwards.

[0139] The sensor spring 310 in the linear sensor 294 presses the guide 296 towards the tip of the sensor 292 with a relatively low force. Thus, the movement of the tip actuator only slightly affects the linear sensor 294.

[0140] TJF 290 in one embodiment positioned on one of the members of the torque device 10 and 68 in the torque device 1. When the torque device 1 is moved in a vertical direction relative to the tool connector 2 TJF 290 reads the surface of at least the first and second parts pipes 4, 6. The position of the hard band 274 of the seat 270 is determined and the jaws of the clamp 152 of the second member of the torque device 68 are, as desired, positioned as close as possible to the hard band 274.

[0141] Reference point 312 may be on the arm of the tool connector 280 to overcome some reference disadvantages of some TJF 290.

[0142] The pipe tally system 320, known for use in the extraction of oil, comprises a database 322, see Fig. 33, usually in the form of an electronic database. The measuring system 320 often includes information such as the type of pipe, here illustrated as the first and second pipes 4, 6, the so-called arm-to-arm length G and the weight of each pipe 4, 6.

[0143] Since the type of pipes 4, 6 is identified in the construction of the chain, which is not shown, the length and weight of said chain can be updated by a known measurement system in the art as new pipes are added.

[0144] Torque device 1 and TJF 290 may have a separate or common control system 324, which in one embodiment includes at least one torque control system 260, or a measuring control system 300.

[0145] The control system 324 is connected to the torque device 1 and TJF 290. Such connections contain the necessary, not shown, power and hydraulic hoses as well as control cables.

[0146] Data on pipes 4, 6 and tool connector 2 stored in a measuring system which in one embodiment is used by the torque device 1 and detecting / mapping the "tool connector finder" (TJF) 290 profile may include, but is not limited to to:

General data: pipe type 4, 6 socket type 270 plug type 278 connection type / pipe type hard band yes / no

P0 / 2939 / JDN calibration factor (s) [0147] Dimension data of pipes 4, 6 and tool joint 2: Dimensions may be general for pipe type and / or specific to actual pipe / tool joint as it is , because the tool connectors can be re-processed, the hard band can be re-applied, etc. The connector can be dimensioned according to the requirements for the socket and plug.

G - total length from shoulder to shoulder 0t - tool connector diameter 0p - pipe diameter

A - distance from thickening to the arm B - distance of the cylindrical face C - distance of the base of the hard band to the arm D - distance of the top of the hard band to the arm [0148] Derived dimensions that can be calculated in the control system 324 of the torque device 1 / TJF 290:

Hard band width = C - D

Slope of thickening = (0t - 0p) / (A - B)

E = reference distance for TJF 290 = A - (registered offset * thickening slope) [0149] Registered offset: because some "tool connector seekers" may have a "dead band" F in which profile changes will not be registered, the recorded offset is related to these specific TJF 290. Specific information about this and other torque device 1 or TJF 290 will likely be stored in or entered into torque device 1 or the TJF 290 control system 324 rather than in the 322 measurement system database.

[0150] Torque data stored in database 322:

The date and time of the torque work.

Shaft data when desired.

The maximum, minimum and recommended torque values ​​for creating tool connector 2. They can be stored in the measuring system database 322 and transferred to the control system 324 of the torque device 1 or directly provided by the operator 326 to the control system 324.

[0151] The set torque input by the operator 326 may be stored in the torque device control system 324 or in the measurement system database 322.

[0152] In general, the inputs can be provided by the operator 326 or read from an available source, such as a radio frequency identification (RFID) reader 328 located on the torque device 1 or on the TJF 290.

[0153] The control system 322 receives information about the actual torque and the corresponding rotational position 86 of the first member of the torque device 10 as mentioned above. The measured torque-rotation information in one embodiment is stored in the measuring system database 320 and refers to the actual tool joint 2.

[0154] Measurement data that can be stored in the measurement system database 320:

Real creation torques that are recorded by the torque control system 260 and output to the historical tool connector database, which can be part of the 322 measurement system database or can be a separate database, not shown here.

The expected or optimal split torque can be stored as an absolute value or as a derivative of the function of the actual torque of creation.

The actual split torque recorded by the torque control system 260 and output to the historical connector database. Optimal torque / rotation curves can be stored in the measuring system database if the associated torque device 1 is compatible.

Actual torque / rotation curves can be stored in the historical measuring system database.

Over range warnings can be saved.

[0155] Tube profiles for storage in database 322:

- Operational measurement data.

- General and detailed dimensional information of the connector as mentioned above.

- Measured dimensional information, as mentioned above, from TJF 290.

[0156] Based on the information available for the control system 324, the control system may in one embodiment create leads for the operator 326. The output may include: actual torque compared to base torque, warnings, tick status, TJF 290 outputs and tool connector diagnostics .

[0157] Real torque / rotation curves can be processed in the tick control system in real time and with over range warnings.

[0158] Information about the historical measurement system database may be sent to and used by the maintenance planning system.

[0159] Additional benefits and possibilities of using the integration of torque-rotation information and profiles in the measurement system 320 are discussed in the general part of the description.

VP / 2939 / JDN

EP 2 753 785 B1