Axial extension by means of three cam clutches for creation of gripping tool with improved operating range and lifting capacity

FIELD: machine building.

SUBSTANCE: invention refers to tubular products gripping and manipulation tool. Gripping tool has gripping surface that is borne against movable gripping elements and control mechanisms for radial movement of the gripping surface from retracted to extended position. Gripping tool includes control mechanisms comprising at least one control mechanism with three cam clutches, which in its turn includes drive cam clutch receiving the input rotation and tending to the rotation transfer; intermediate cam clutch receiving the input rotation only from drive cam clutch; driven cam clutch receiving the input rotation only from intermediate cam clutch; drive cam pair acting between drive cam clutch and intermediate cam clutch so that input rotation is transmitted by drive cam pair from drive cam clutch to intermediate cam clutch, and driven cam pair acting between intermediate cam clutch and driven cam clutch so that input rotation from intermediate cam clutch is transferred by driven cam pair to driven cam clutch.

EFFECT: providing the control of axial and radial movements of gripping tool surface.

10 cl, 13 dwg

 

This invention relates preferably to such options, where you must capture tubular products and pipe columns, to perform manipulation and lifting tool connected to the rotator drilling rig or design application of reactive efforts to ensure the transmission of axial and torsional loads on the captured tubular section or from it. In drilling land, construction and repair of wells with drilling rigs and installations underground repair of wells this invention relates to a wedge grips, and more specifically, on drilling rigs with top drives, used in instruments descent tubular products attached to the top drive for gripping close to it section of pipe columns, up in the wellbore that are deployed in it or derived from it. Such instruments descent tubular products are various functions that are necessary or useful for these works, which includes a quick connection and release, lifting, pushing, rotating, and applying the fluid under pressure in the tubular string and the release from it. This invention created the governance arrangements for the expansion or improvement of the capture range of such instruments descent tubular products.

Until recently, mechanical is the cue trumpet keys used in the prescribed way for the descent of the columns of the casing or drill pipe in oil wells and recovery wells in cooperation with the lifting system of the rig. This method using mechanical pipe wrenches provides a relatively efficient Assembly of such pipe strings, comprising pipe sections or parts abutting threaded ends, by screwing mating threaded ends (bond) with the formation of the threaded joints between successive pipe sections at their building on the column installed in the wellbore; or in the reverse process of removing and dismantling (unclamping). But this method using mechanical pipe wrenches at the same time shall not be of other useful functions, such as rotation, indentations or filling fluid medium, after extension pipe on the column or remove it from the column, and during the descent or ascent of the column in the wellbore. Descent tubular products using pipe wrenches are also usually requires staff working in areas of increased risk, such as the rig floor or, even more dangerous on the drilling floor, the so-called 'balconies to work with casing pipes'.

The emergence of drilling rigs equipped with top drives, gave a new way of running pipe products and, specifically, of the casing, where the top drive equipped with so-called 'tool descent tubular products top drive' to capture and, if possible, create a seal between the nearest section of the pipe and the hollow shaft of the top drive. (Here it should be understood that the hollow shaft of the top drive, in General, is composed of such components of the drive columns, which you can attach to it, the far ends of which effectively act as an extension of the hollow shaft.) Therefore, we have developed various devices, in General, are designed to run 'of the casing top drive'. The use of these devices in cooperation with the upper drive enables the lifting, rotation, penetration and filling of the casing pipe mud during the descent, thus removing the limitations associated with the use of mechanical pipe wrenches. At the same time automation exciting mechanism, in Association with the specific advantages of top drive, reduces the required participation of staff in comparison with the descent using mechanical pipe wrenches and, thus, increases the security.

In addition, the manipulation of the casing and the descent from the use of such a tool descent tubulars using a top drive, the weight of the column must be transferred from the upper drive support device when near or in the work section of the pipe increasing or removed from the collected columns. This function usually performs 'ring wedge grip', driven on the op perate axial load of the gripper, use 'V-grip' or jaws, placed in a cavity 'case V capture'through which the lower casing, where the casing wedge grip has a channel in the shape of a truncated cone with decreasing down in diameter and rests on the rig floor or installed in the drill floor. The V-grip, acting as the ring wedges between the section of pipe near the end of the column and the inner surface in the shape of a truncated cone shell V-grip, with the application of traction load grabs the pipe, but moves or slides down and, thus, the radially inward on the inner surface of the shell V-grip when the weight of the column is transferred to the capture. Radial force between the wedge grip and casing pipe, thus, 'automatically generated' or 'automatically enabled' axial load, i.e., when considering towing capacity of the dependent variable and the weight of the column of the independent variable, there is a control loop with positive feedback, where the independent variable is the weight of the column is rigidly transmitted over the feedback channel, driving a radial grip force, which monotonically valid driving traction ability or resistance to sliding, which is the dependent variable. Similarly, there must be opposition steep is the overarching point of fastening and unfastening, included in the section of the pipe, near the end of the assembled column. This function is usually performed pipe wrench having seizures, connecting with the nearest section of the pipe, and a lever attached to a connecting link, such as a chain or cable, the design of the rig to prevent rotation and, thus, create a counter torque with no response wedge grips in the case V capture. The grip force of such pipe wrenches likewise usually 'automatically generated' or 'automatically enabled' positive feedback on the applied load torque.

In General, an exciting tool patent application PCT CA 2006/00710 and U.S. application 11/912,665 can be described as exciting tool that includes a chassis having a load bearing adapter attached to transfer axial load on the rest of the body, or, in short, the main body, and carrying load the adapter is made with the possibility of a constructive connection with the rotator of the machine or frame transmission reactive efforts, exciting layout, which bears the main body having a gripping surface, and an exciting layout, equipped with a means of switching to radial stroke or movement of venutolo is the provisions in the position of connection radial connection of the traction load surface capture either the inner surface or the outer surface of the product in response to relative axial movement or axial stroke of the main body, at least in one direction relative to the surface of the grip. Created a control mechanism acting between the chassis and exciting layout, which during the rotation, at least in one direction carrying the load of the adapter relative to the surface of the grip, gives as a result of axial displacement of the main body relative to the exciting layout to move exciting layout of venutolo position of the compounds according to the action of the tools included in the work.

This exciting tool, thus, uses mechanically incorporated into the work capture mechanism that creates its exciting force in response to activation of axial load or axial stroke of the layout of the capture and incorporation in the work, arising from, or in conjunction with the application of an external axial load and external load torsion or independently of them, in the form of application of the right or of the left torque loads transmitted through the tool from carrying the load of the adapter body composition on the surface of the capture exciting layout, combined traction load with the product.

It should be clear that the usefulness of data or other similar exciting tools options is what her range of product sizes, usually expressed as minimum and maximum diameters of tubular products that can be placed between the surfaces of the grip in the fully retracted and fully extended the provisions of this exciting tool, i.e. radial size and radial stroke exciting surface. The usefulness of this exciting tool can be improved if the tool will be able to accommodate products with sizes over a wide range. The present invention is directed to satisfying this need for applications where increased radial size and radial stroke are useful, which often occurs when adaptation exciting tools for descent tubular goods oil country tubular goods.

According to a broad aspect of the present invention the mechanisms that control extension for use in an exciting tool in ensuring the radial elongation of the stroke and size of products that can be placed in this exciting tool having a gripping surface, which are movable gripping elements. The invention includes a control mechanism with three jaw clutches Cam pairs, providing dvuhoborotny control axial stroke, and additional Cam control mechanisms causing R is Dalny stroke the surface of the gripper tool as a function of axial travel.

The control mechanism with three jaw clutches includes:

leading Cam clutch,

intermediate the Cam clutch,

the driven Cam clutch,

leading Cam couple acting between the leading Cam clutch and the intermediate Cam clutch, and

the driven Cam pair, acting between the intermediate Cam clutch and driven Cam clutch.

Preferably, the leading Cam pair is made with the possibility of action, only causing axial stroke, as a function of rotation at the first rotation direction, and the driven Cam pair in the second direction of rotation, the separation dogovornogo control two Cam pairs leads to the establishment of greater axial stroke and, accordingly, the radial stroke of the surface capture than is possible using one Cam pair when dvuhoborotnym the control mechanism.

Data and other characteristics of the invention shall become clearer from the following description, which made reference to the accompanying drawings for illustration only, not intended in any way to limit the scope of the invention or specific shows options for implementation. In the drawings shows the following:

In Fig. 1 is an isometric view with a partial cutout of a simplified version of LW the axle dvuhoborotny included in the tool descent tubular products with external capture created in the configuration architecture with one Cam couple shows how it should look with the application of the right torque.

In Fig. 2A diagram of the basic configuration architecture with one Cam pair Fig. 1 in a two-dimensional representation shows how it should look with the application of the right torque.

In Fig. 2B is a diagram of the architecture of Fig. 2A in a two-dimensional representation shows how it should look with the application of the right torque.

In Fig. 3 schema architecture with three jaw clutches in a two-dimensional view is shown without the application of torque.

In Fig. 4A, the circuit architecture with the three jaw clutches Fig. 3 in a two-dimensional representation shows how it should look with the application of the right torque.

In Fig. 4B, the circuit architecture with the three jaw clutches Fig. 3 in a two-dimensional representation shows how it should look with the application of the left torque.

In Fig. 4C, the circuit architecture with the three jaw clutches Fig. 3 in a two-dimensional representation shows how it should look in an exciting tool with applied axial elongation.

In Fig. 5A, the circuit architecture with the three jaw clutches with the Cam by a pair of lifting lugs in a two-dimensional representation shows how it should look with the application left to Otsego moment.

In Fig. 5B, the circuit architecture with the three jaw clutches Fig. 5A with the Cam by a pair of lifting lugs in a two-dimensional representation shows how it should look with a small right turn to lift stops in the neutral position.

In Fig. 5C, the circuit architecture with the three jaw clutches Fig. 5A with the rise of thrust in a two-dimensional representation shows how it should look with the application of the right torque.

In Fig. 6A, the circuit architecture with the three jaw clutches Fig. 3 with the latch in a two-dimensional representation shows how it should look in a fixed position.

In Fig. 6B, the circuit architecture with the three jaw clutches Fig. 3 with the latch in a two-dimensional representation shows how it should look with the application of the right of torque, with detached lock.

In Fig. 6C, the circuit architecture with the three jaw clutches Fig. 3 with the latch in a two-dimensional representation shows how it should look disconnected from the latch, and with the application of the left torque.

In Fig. 7A, the circuit architecture with the three jaw clutches Fig. 3 with lock with lock in a two-dimensional representation shows how it should look in a fixed position.

In Fig. 7B, the circuit architecture with the three jaw clutches Fig. 3 with the latch with the possibility blokirovku a two-dimensional representation shown, how it should look with the application of the right torque with detached lock.

In Fig. 7C, the circuit architecture with the three jaw clutches Fig. 3 with lock with lock in a two-dimensional representation shows how it should look with detached retainer and attached the left torque.

In Fig. 7D circuit architecture with three jaw clutches Fig. 3 with lock with lock in a two-dimensional representation shows how it should look with detached retainer and compression applied from the connection on the driven Cam pair.

In Fig. 7E architecture diagram with three jaw clutches Fig. 3 with lock with lock in a two-dimensional representation shows how it should look with detached retainer and compression applied from the connection on the leading Cam pair.

In Fig. 7F the architecture diagram with three jaw clutches Fig. 3 with lock with lock in a two-dimensional representation shows how it should look for the option with the locked latch, and applied the right torque.

In Fig. 8 appearance of the tool descent tubular products architecture with three jaw clutches shows how it should look in a fixed position.

In Fig. 9 is a sectional view of the tool down the pipe the output product architecture with three jaw clutches shows how it should look in a fixed position with placement inside the middle of the end product.

In Fig. 10A appearance layout with three jaw clutches shows how it should look in a fixed position.

In Fig. 10B is a sectional view layout with three jaw clutches shows how it should look in a fixed position.

In Fig. 11A appearance part of the Assembly of the locking mechanism includes a leading Cam clutch, the ring lock and key lock, shows how it should look in a fixed position.

In Fig. 11B partially broken isometric view of part of the Assembly of the locking mechanism includes a driven Cam clutch, the ring lock and key lock, shows how it should look for a disconnected position.

In Fig. 11C external layout view of a part of the latch that includes a leading Cam clutch, the ring lock and key lock, shows how it should look for a disconnected position.

In Fig. 12A appearance layout with three jaw clutches shows how it should look with the application of the right torque.

In Fig. 12B a sectional view layout with three jaw clutches shows how it should look with the application of the right torque.

In Fig. 13A appearance layout with three jaw clutch is shown, how it should look with detached retainer and attached the left torque.

In Fig. 13B a sectional view layout with three jaw clutches shows how it should look with detached retainer and attached the left torque.

Exciting instrument described in patent application PCT CA 2006/00710, consists of three main interacting components or configurations: 1) the chassis, 2) exciting the layout, which bears the chassis and 3) a control mechanism acting between the chassis and exciting layout. The chassis, in General, creates a constructive relationship of the component parts of the tool and includes a carrying load the adapter, whereby the load of the rotator of the machine or frame transmission reactive effort is transmitted to the remaining part of the Assembly housing or main body or from them. Exciting layout has a gripping surface, the layout is the main case body composition, and layout provided with a means of radial stroke or movement of the surface of the capture of venutolo position of the connection in response to relative axial movement or axial stroke for radial and traction connection of the product with the engagement surface. Exciting layout, so there is AK included in the working axial load or axial motion capture element.

The main body is installed coaxially relative to the product to create an annular space in which is to be included in the work of the axial passage, an exciting layout, coupled with the main body. Surface capture breathtaking composition adapted for conformal, distributed around the circumference and total resistance, traction connection with the product. The means of effecting radial stroke exciting surface, which carries an exciting layout made with the possibility of binding relative axial displacement or axial running, at least in one axial direction, with the radial offset or radial speed of the surface of the grip to the product correlated with axial and total confrontation radial efforts, this raises so that the radial grip on the surface of the grip provides a response axial load and torque in the product, where distributed radial force grip has an internal counter, the device comprises a driven axial load, the capture mechanism, where the axial bearing the load is distributed between the rotator of the machine or frame transmission reactive efforts and product; freight adapter, the main body and the capture element,in General, the current sequence.

The control mechanism acting between the chassis and exciting layout made with the possibility of binding relative rotation between the load bearing adapter and the engagement surface with axial stroke exciting composition and, consequently, the radial speed of the surface of the grip. Included in the working axial load capture mechanism, therefore, is arranged to provide relative rotation between one or both bearing the axial load of the joints between the cargo adaptor and the main body or the main body and the capture element, the relative rotation is limited to, at least one included in the operation of the rotation control mechanism linking relative rotation between the load adapter and a gripping surface with axial stroke of the capture element and, consequently, the radial speed of the surface of the grip. The control mechanism or mechanisms may be performed to create this relationship between the rotation and the axial passage in numerous variants, such as the mechanism with the swing arm or swing housings acting between the chassis and exciting layout, but can also be made in the form of Cam pairs acting between the at the gripping elements, and at least one of the following: the main body or carrying load adapter for immediate perception, thus, the transmission of axial and torsional loads, causing or tending to cause rotation and maintaining the development of radial grip force. Cam couples acting, in General, the method of using the Cam clutch and moving on Cam coupling copier having a contact surface made in the preferred embodiment, to associate their combined relative rotation at least in one direction, with the axial stroke of the capture element toward sealing engagement, when this axial stroke, thus, has a similar effect from the axial passage created axial load borne by the capture element, and operates in Association with it. The use of relative rotation between the spinner machine or frame transmission reactive efforts and the engagement surface in contact with the product, at least in one direction, thus, causes a radial stroke or radial displacement of the surface capture in connection with the product with correlative axial force, torque and radial force when this occurs so that the radial grip on the surface of the grip provides excellent the provides reaction torque in the product, the device contains an inclusion of the work torsional loads so that, together with the involvement of axial load capture mechanism is automatically activated in response to the combined loading on two axes, at least one axle and at least one tangential direction or the direction of the swirl.

Also according to the patent application PCT CA 2006/00710 layout with jaw clutches can be used in various devices, as summarized in the application in table 1, where the data layout with function "Cam couplings", in table 1, creating relative axial movement between leaders and led jaw configurations as a function of the applied relative rotation; this relationship is controlled by selecting the local step or angle of the helical line, acting on the junction of the Cam pairs. If the action should be dvuhoborotnym (to engage with the left and right spins) and is provided with a Cam arrangement, consisting of one pair of Cam shown and described, as sawtooth profiles between mating profiled ends in a common cylindrical and coaxially aligned rigid housings, as shown in Fig. 11B (showing the Cam clutch used in the basic architecture or Configuration 1 tab is itzá, 1, how can she look in the external exciting tool), which is re-presented here in Fig. 1, showing the arrangement 1 Cam clutches with a leading Cam clutch 2 and the driven Cam clutch 3 creating Cam couple 4, they can form with your application right rotation. Here used the name "master" and "slave" for Cam clutches for convenience in describing the relative displacements and forces. This should not be limiting in respect of the application because, in General, described the Cam system can invert.

In Fig. 2A layout 1 Cam clutches are shown schematically in a two-dimensional representation, where the axial and tangential directions are shown as the ordinate and abscissa, respectively, in the graph of Fig. 2A. Tangential position, thus, represents the location on the circle, and the tangential displacement is a rotation. Cam pair 4 presents multiple mating right helical load bearing surfaces 5, shown here as two passes with intermediate elevation angle of the helical line, and left helical load bearing surfaces 6 with two approaches, shown here with a relatively low elevation angle of the helical line, i.e. a smaller pitch than the helical bearing Naga is the DCU surfaces 5, where the intersection of the helical load-bearing surfaces 5 and 6 form the projections or peaks 7. It is clear that when you increase the right relative rotation, left helical load bearing surface 6 are connected, the length "C" of tangential contact in connection decreases, while the relative axial breeding Z (axial stroke between the leading and the trailing jaw clutches increases before joining position limits, where additional rotation can give, as a result, the installation of the peaks on each other. Since the Cam pair must also pass the load actually occurs restricting position when the magnitude of the contact is insufficient to carry the required load, providing the total displacement, represented by the vector R shown on the graph, where the axial component of R is Z, i.e. axial move. In Fig. 2B, this limit is shown for layout 1 Cam clutches, how it should look in the applications left rotation leading to the Cam sleeve 2 relative to the driven clutch 3, causing the action right helical load-bearing surfaces 5, where the total displacement is represented by a vector of L. Thus, there are limits axial stroke and load capacity (represented by the size of Z and C respectively in Fig. AI 2B), a single Cam pair dogovornogo rotation, especially when combined with other, parallel to the existing, structural parameters, such as preferred step or the corners of the lifting screw line managers as the actuation to the left and to the right, as is clear from a comparison of the pair of Cam 4 in Fig. 2A and 2B when the right and left spins, respectively. Although such a configuration with one Cam pair, creating axial stroke as a function of applied relative rotation in two directions, provide significant utility in some embodiments, the application requires increased speed and capacity.

One purpose of the present invention is to provide means for reducing or effectively eliminating this restriction in the working range and load carrying capacity, characteristic of single Cam pairs, operating in two directions, and means adapted to any of the control mechanisms, referred to as "Cam" in table 1 PCT CA 2006/00710. In Fig. 3 improved architecture of Cam clutches of the present invention (also on the schematic two-dimensional representation, where the axial and tangential directions are shown as the ordinate and abscissa, respectively) gives the arrangement 10 with three jaw clutches with a leading Cam clutch 12, the driven Cam clutch 13 and at least one intermediate is blackboy clutch 14 for action between the leading Cam clutch 12 and driven Cam clutch 13; and, therefore, is referred to in this document architecture with three jaw clutches. The leading Cam pair 15 is made with the possibility of action between the leading and intermediate jaw clutches, 12 and 14, respectively, and driven Cam pair 16 is made to act between the intermediate and driven jaw clutches 14 and 13 respectively. The leading Cam 15 consists of a pair of connecting lugs 17 formed of a relatively steep angle helix (here vertical) interface surfaces 18 stops and the relatively low elevation of the left helix interface surfaces 19 of the inclined lugs, where mating helical surfaces 19 of the inclined lugs also operate in parallel abutting load-bearing thread 20. Driven Cam pair 16 consists of connecting the load-bearing inclined sections 21, formed by the junction at a relatively steep angle helical surfaces 22 of the inclined lugs (here vertical) and carrying the load right mating helical mating surfaces 23 of the inclined lugs, shown here with an intermediate elevation helix (similar to bearing load right helical surfaces 5, shown for the Cam pair 4 in Fig. 1).

In Fig. 4A by the azan arrangement 10 with three jaw clutches, how it should look with a certain right rotation, causing the relative displacement of the leading pair of Cam 15, initially causing dilution of the surfaces 18 stops and when sufficient rotation also contributes to the breeding of the surfaces 19 of the inclined lugs so that the load shall be fully mating threads 20 of the bearing load on the offset or within the range specified by the vector R. it should Now be clear that when the right axial rotation speed and load of the bearing load of the pair of Cam 15 is not limited useful contact length of the helical surface 19 of the inclined lugs, but only limited load bearing threads 20, which can easily take to create a sufficient length connection and strength to provide adequate strength with virtually unlimited axial stroke, effectively eliminating these restrictions for design purposes. In fact, the surface 19 of the inclined lugs are redundant and do not need the connection.

As also shown in Fig. 4A, the angles of ascent helix bearing sloping ground surfaces 21 and 22 of the inclined lugs forming the driven Cam pair 16, is selected to meet the elevation angle of the helical line of the load-bearing threads 20, and other variables, such as coefficient of friction, candelino be clear to a person skilled in the art so that under the action of nominating or retractor right rotation no displacement occurs in the driven Cam pair 16.

In Fig. 4B shows the arrangement 10 with jaw clutches, how it should look with the application of the left rotation leading the Cam clutch 12 relative to the driven clutch 13. In this case, the driven Cam pair 16 is active and operates in a manner analogous to that described above for the leading Cam 15 pairs, with opposite directions of the elevation angle of the helical line of the load-bearing sloping ground. Application left rotation leading to the Cam sleeve 12 causes the dilution of the surface 21 inclined lugs, and correlatively sliding contact on the load-bearing screw-shaped surfaces 23 causes the displacement of the intermediate clutch 14 and the leading of the Cam clutch 12 axially upward relative to the driven clutch 13, creating the offset within the specified vector L. the axial load and the load from the left of torque, which carries arrangement 10 with three jaw clutches, reacts leading Cam pair 15, in which the lugs 17 through selection of the elevation angle of the helical line on the contact surfaces 18 stops and the installation may be used to control how the response to the load through privode the Yu Cam couple 15 to regulate the voltage and prevent zakanchivaya torsional loads on the threads of the intermediate clutch 14 with the leading Cam clutch 12 due to their connections on the load-bearing thread 20, i.e. frictional locking the screw type nut and bolt. Also, similar to the behavior when the right rotation, as described above, the elevation angle of the helical line of the load-bearing inclined sections 21 is chosen corresponding to the elevation angle of the helical line of the load-bearing threads 20 so that under the action of the left rotation to move forward or retracting no offset occurs in the leading pair of Cam 15.

It should now be clear that the arrangement 10 with three jaw clutches created Cam pairs (leading Cam pair 15 and the driven Cam pair 16): the first is active and generates axial stroke with right-hand rotation, when the second is static; and the second active and creating axial stroke in the left rotation when the first is static.

The comparison of the vectors R and L offset in Fig. 2A and 2B with the vectors in Fig. 4A and 4B, respectively, shows that for comparable geometrical parameters of the axial stroke of greater magnitude can be obtained as when the right and left rotation with the leading and the trailing Cam pairs 15 and 16 (Fig. 4A and B) in the architecture 10 with three jaw clutches, than you can get one that runs in two directions, a Cam pair 4 (Fig. 2A and B).

As also shown in Fig. 4B, for the above ideas include load-bearing threads 20 in the composition of the leading Kul is ckovo 15 pairs should be clear, that you can create load bearing threads 20, to work in cooperation with mating bearing the load of the helical surfaces 23 to increase speed and capacity; however, in some embodiments, applying the tools of descent tubular products may be preferable to provide the free cultivation of the leading and trailing Cam clutches 12 and 13, respectively, which provides the configuration shown in Fig. 4C, where the intermediate Cam clutch 14 remains connected load bearing threads 20 with the leading Cam clutch 12, but not connected, thus, the driven Cam clutch 13, providing free dilution may be required to ensure actuation of the gripper with the application of an axial load without at the same time the current rotation, when the arrangement 10 with three jaw clutches are used, for example, in basic Configuration 1) the exciting architecture of the tool shown in Fig. 1.

As an intermediate architecture (not shown), where the bearing load of the thread 20, which connects the driven Cam clutch 13 and the intermediate Cam clutch 14 are required, and still requires a certain degree similar freedom for axial breeding, bearing the load of the thread 20 can provide significant side zip pocket wit the gap. It should be clear to a person skilled in the technical field for a single thread this lateral clearance is limited only by the pitch with a value less than the required thickness of the crests of the thread, so significant free axial breeding can be obtained for applications where it is possible to use a relatively larger step, i.e. applications where low elevation angle of helix is not required.

As an additional intermediate architecture (not shown) the two Cam pairs can be formed as the inclined surface stops, still bearing the load of the thread 20 (with a small lateral gap)that can be called architecture with four jaw clutches (not shown). Architecture with four jaw clutches can be performed with the fourth kulacom component, with the constraint that provides the axial movement but preventing rotation relative to the driven clutch, and rigidly attached to the layout of the grip so that when the release latch arrangement with jaw clutches supports the possibility of free axial stroke for connection with the product under deflective load. Such a device can be useful if you want to move more than you can take in the architecture with three jaw clutches (specifically about the found device driven Cam pair).

Also in Fig. 4B shows the summation of the axial height and, consequently, the carrying capacity lugs 17, which is a function of the step or elevation angle of the helical line selected for mating load-bearing thread 20 (and, similarly, the surface 19 of the inclined lugs), so for applications where low elevation angle of the helical line of the thread is preferred, it becomes more difficult to ensure sufficient strength for the response on the left of the torsional load, which is achieved by means of lugs 17 with correlative small axial height. For such applications an additional objective of the present invention is to provide means to overcome this limitation by replacing the intermediate clutch 14 in the arrangement 10 with three jaw clutches, as shown in Fig. 5A, the arrangement 30 with the intermediate jaw clutches acting between the leading Cam clutch 12 and driven Cam clutch 13. Arrangement 30 with the intermediate jaw clutches consists of the auxiliary ring 31 of the lifting lugs and the pipe 32 with the intermediate Cam clutch, where the Cam pair 33 with lifting lugs made with the possibility of action between the ring 31 with supports and the pipe 32 with the intermediate Cam clutch. Cam pair 33 with lifting lugs has a surface 34 raised acronyme plots and surface 35 with a raised catchers. In General arrangement 30 with the intermediate Cam clutch operates in a manner analogous to intermediate Cam sleeve 14 in the case of application of the right and left rotation, as shown in Fig. 4A and 4B and described above for composition 10 with three jaw clutches. If you compare shown in Fig. 4B and 5A action ring 31 of the lifting lugs in the case of application of the left torque is obvious where the left torque causes the movement of the ring 31 with stops up on the surfaces of 34 raised sloping ground, making a full connection surfaces 18 stops, so that the combined height of the surfaces 18 stops, thus, becomes more, if use architecture with ring lifting lugs. Also, it should be clear that the elevation angle of the helical line of the raised surfaces sloping ground is chosen consistent with the elevation angle of helix surfaces 18 of the stops to create the specified full connection surfaces 18 stops at the left rotation, and, similarly, the combined length of the surfaces 34 raised sloping ground correlative made to create sufficient strength to support the load, which react with the surface 18 of the stops. In Fig. 5B shows the arrangement 30 with three jaw clutches with a moderate right-hand rotation, the ring 31 of the lifting lugs shown fully the TEW slipped down over the surface 34 of the raised inclined sections (Cam pair 33 in the fully retracted position), the movement may be variously constructed as: previous contact with the surfaces 19 of the inclined stops when the right rotation (where the elevation angle of the helical line of the surface 19 of the inclined lugs choose consistently with elevation angle of helix catching raised surfaces 34 for creating such a move); gravity; or deflection of springs (not shown), applied pulling force relative to the tube 32 with the intermediate jaw clutches. In respect of the provision of a Cam pair 15 is made so that the surface 18 of the lugs have some degree of overlap, large enough to 'salamouny', if the applied left-hand rotation, but 'passing away' in case of application for additional right rotation, which may cause additional axial stroke with limit load-bearing thread 20, as shown in Fig. 5C.

As shown in Fig. 4C, in some embodiments, the application must limit the free axial breeding provided between leaders and led jaw clutches 12 and 13, respectively, the creation of the latch, specifically, to support the insertion and removal of a fully mechanical exciting tools, as described in PCT CA 2006/00710. Therefore, an additional aim of the present invention is to provide a latch function is relevant in architecture with three jaw clutches, supporting the fixation of the leading Cam clutch 12 to the drive Cam sleeve 13, as shown in Fig. 6A, where the latch 40 is shown with the arrangement 10 with three jaw clutches, again in a two-dimensional representation, where the radial plane, which carried out the signs of the retainer 40, in General, different from the above indication that the link 10 with three jaw clutches. The ring 41 of the latch is, in General, a tubular body attached firmly and coaxially mounted on the driven Cam sleeve 13 having a right helical grooves 42, which are tightly fixing pins 43 of the latch, with the pins 43 of the clamp is rigidly attached to the drive Cam coupling, with this device, the retaining ring 41 of the latch to move only between the axial extended and retracted position relative to the driven clutch 13, which sets the course of the retainer in a spiral path with a specified length of spiral grooves 42 with respect to the length of the pins 43 of the retainer. Cam a pair of latch 47 is made to act between the ring 41 of the clamp and the leading Cam clutch 12 and is formed, in General, mating profiled hooks 44 of the retainer having a selected height somewhat less than the selected speed latch, and having a rear surface 45. The hooks 44 earstuds (ejew-g is as shown in the position of the connection of Fig. 6A and in such position to prevent axial breeding leading the Cam clutch 12 and driven clutch 13, the axial load, which may otherwise their breed, reacts leading Cam clutch 12 through the hooks 44 of the retainer ring 41 lock and keys 43 of the retainer held in the spiral grooves 42 and pins 43 of the latch on the driven Cam sleeve 13 to which the pins 43 of the latch is attached. However, when the right rotation, as shown in Fig. 6B, the hooks 44 of the latch strive to detach, and the ring 41 of the latch is free to retract, secured by pins 43 in the right helical grooves 42, where the retraction can be created variously as: gravity, deflection of the spring 46 acting between the ring 41 of the latch and driven Cam clutch 13; or sufficient rotation, the contact rear surfaces 45 hooks angles rise helix abutting the rear surface 45 of hooks, selected from, respectively, the elevation angle of helical grooves 42 to generate pulling forces. With the application of the left rotation and the Cam pair 16, stacked, as shown in Fig. 6B, i.e. without axial cultivation, sufficient traction hooks 44 of the clamp is also made with the possibility of re-commit hooks 44. However, if the leading Cam the I clutch 12 is lifted first, determining axial breeding, sufficient to prevent connection of the hooks 44 of the latch, and then make a left rotation, as shown in Fig. 6C, re-recording is stopped and the Cam pair 16 is active, determining axial stroke.

The process shown in Fig. 6A-6C and described above composition with jaw clutches with the beginning in a fixed position can be described in two stages as follows:

1. The installation of the tool (in the product).

2. Turn to the right (to detach the clamps and connections leading Cam pair).

In the case of using the tool for breaking links with the connection of the driven Cam pair requires the following two additional steps:

3A. The pickup on the instrument.

3b. Turn left (to connect the driven Cam pair).

Workflow disconnect the tool from the workpiece is similarly simple and requires two or three steps from the inclined sections of the fastening or unfastening, respectively, consisting of the following:

1. The installation of the tool.

2. Turn left (for retracting build engagement and connection release).

Where to commit the tool from the driven Cam pair requires one the following additional step:

1a. Turn right to join a leading Cam pair,then go to step 1.

Provided that the simplicity of the process is not predictable or not a random event can lead to the simultaneous application of sufficient left torque, rotation and compression tool to connect the clamp, and if such events are sufficiently frequent, the risk of unplanned fixation and, therefore, detach layout capture from the product may be unacceptable. In such embodiments, applications where it is necessary to limit the free axial breeding provided between the leading and the trailing sleeves, the creation of the release, specifically to support the insertion and removal of a fully mechanical exciting tools, it may also be necessary to prevent accidental connection of the latch. In this regard, an additional objective of the present invention is to provide a locking mechanism that is functionally associated with the architecture with three jaw clutches and retainer shown in Fig. 4 and 6A-6C, respectively. Additional preferred implementation of the present invention shown in a two-dimensional diagram in Fig. 7A-7F and described in this document. This option is integrated mechanical locking device, configured to enable the lock in action link with jaw clutches f is, 6A-6C. The process is equipped with a locking device layout with jaw clutches can be described in the following six stages:

1. The installation of the tool (in the product).

2. Turn to the right (to detach the lock).

3. Pick-up (to release the hooks of the latch).

4. Turn left (to connect the driven Cam pair).

5. Installation tools (spring compressor).

6. Turn to the right (for the connection of the locking mechanism, connections leading Cam couples, and capture products).

Where required the following additional step for breaking links:

7. Turn left (to connect the driven Cam pair and capture products).

The process for detaching the locking mechanism and the fixing of the tool from binding also requires the following six stages:

1. Installation (for connection leading Cam pair).

2. Turn left (to detach the casing and unlock tool).

3. Pick-up (for break release).

4. Turn right (turn back the leading Cam pair).

5. Installation to connect the leading Cam pair).

6. Turn left (for retracting the capture and layout tools with lock).

If you start from the connection driven Cam pair, you want one next updat the enforcement stage:

1a. Turn right to join a leading Cam pair, then go to step 1.

From the above procedure it is clear that additional steps will reduce the risk of accidental disconnection by increasing the complexity of the operation.

In Fig. 7A shows the architecture with three jaw clutches with integrated mechanical locking scheme with a two-dimensional representation of how it should look with the United latch. Layout with three jaw couplings with lock has a leading Cam clutch 12, the driven Cam clutch 13, the intermediate Cam clutch 14 and the retainer 40. Cam a pair of latch 47 is made to act between the housing 41 of the clamp and the leading Cam clutch 12 and is formed, in General, the hooks 44 of the latch mating profile. Profile 45 of the hook latch on the housing 41 of the retainer includes a stop 61 lock on the top side 62, and the profile 45 of the hook latch of the leading Cam clutch 12 has, in General, mating socket 63 under the focus lock on the bottom side 64 and the free space for the stop block on the upper side 69. The angles of the faces 65 and 66 of the stop of the lock choose together with the angles of the faces 67 and 68 nests under the focus lock and keyed geometry of grooves 42 for the communication lock, remove the lock and release of the body earstuds (ejew-g is and during bonding. The keyways 42 of the housing 41 of lock and keys 43, rigidly attached to the drive Cam sleeve 13 are a pair of 70 faces the lock, consisting of abutting faces 71 and 72 of the lock. The angle of the faces 71 and 72 of the lock choose together with the angle of load-bearing threads 20 to prevent accidental release of the lock due to vibration and reduce the uncertainty of the position of the joint stops 61 lock on the bottom of the profile 45 of the hook latch of the leading Cam clutch 12. Driven Cam sleeve 13 has a spring 73 compression stroke limitation, pre-tense when the latch 40 is cut off, deflecting the spring 46 pushes the face 74 of the housing 41 of the retainer in contact with the stop 75 of the spring. The stiffness coefficient and the initial tension compression spring 73 is chosen in conjunction with the stiffness coefficient and pre-stress deflection of the spring 46 so that the spring 73 is compressed after the initial provisions of the preliminary voltage under load deflection of the spring 46 and any abnormal loads, including the weight of the component.

In Fig. 7B shows the layout with jaw clutches Fig. 7A in the diagram with the two-dimensional representation of how it should look with detached lock and faces of the hooks of the latches in contact, compressing the spring 73 remains fully extended, and it is intact with the body 41 of the latch sets it that face of the hook profile 45 of the hook of the latch are overlapping and sliding connection. The pins 43 are installed in the spiral section 77 the key groove 42 so that the right-hand rotation should cause the disconnection of the profile of the hook latch and left-hand rotation should lead screw slide housing 41 of the latch on the feather key grooves 42 and the connection of the hook profile 45 of the hook of the latch extension deflecting the spring 46 to set the layout in the position shown in Fig. 7A.

In Fig. 7C shows the layout with jaw clutches Fig. 7A in the diagram with the two-dimensional representation of how it should look disconnected from the latch, and with the application of the left torque, with the United spiral sloping surface 23 of bearing load driven Cam pair 16 and the United helical surfaces 19 of the inclined lugs and mating surfaces 18 of the stop of the leading pair of Cam 15.

In Fig. 7D shows the layout with jaw clutches Fig. 7A in the diagram with the two-dimensional representation of how it should look under the action of compressive loads after connecting the driven Cam pair 16. All mating faces as the leading pair of Cam 15, and the driven Cam pair 16 is connected and layout 10 with jaw clutches is under compression. The face 74 of the housing 41 of the latch are connected to the stop 75 of the spring, and compressing the spring 73 is compressed for the position of pre-tension. The pins 43 are installed in the spiral section 77 the key groove 42. The stop 61 of the lock is connected with the socket 63 under the focus lock. The application right rotation leading to Cam the clutch should move the body 41 of the latch in the locked position, causing the faces 71 and 72 70 lock in the connection.

In Fig. 7E shows the layout with jaw clutches Fig. 7A in the diagram with the two-dimensional representation of how it should look with the unlocked latch 40 and the leading Cam clutch 12 and the housing 41 of the latch set for detaching the lock with the application left rotation relative to the driven clutch 13. Sole profile 45 clamps the leading of the Cam clutch 12 ov is connected to the face 65 of the stop 61 of the lock, and left rotation step leading clutch should give, as a result, a similar movement of the body 41 of the retainer relative to the driven clutch 13 and the intermediate clutch 14, followed by working the axial movement of the leading Cam clutch 12 should dictate the movement of the pins 43 of section 76 of the lock screw section 77 the key groove 42.

In Fig. 7F shows the layout with jaw clutches Fig. 7A in the diagram with the two-dimensional representation of how it should look and feel tighter shall be unlocked and the app right rotation leading to the Cam sleeve 12 relative to the driven clutch 13 and the intermediate clutch 14. It is clear that, as shown in the unlocked position as the leading Cam pair 15 and the driven Cam pair 16 can be valid.

It should now be clear that the architecture with built-in mechanical interlock of the present invention is well adapted to stop accidental commit in architecture with three jaw clutches of the present invention due to the reduced likelihood of additional steps required in the sequence of fixation occurring by chance.

It is clear that lock you can block a number of means, including, not as a limitation, mechanical, and hydraulic tools.

Similarly, you can create other fixation device between the leading Cam clutch 12 and driven Cam clutch 13. One such configuration (not shown) deflects the ring 41 of the latch in a normally extended position. When the right rotation ring 41 of the latch tends to push the hooks 44 of the latch from the position of the joint. The latch hooks are in the shape and distribution to prevent partial connections in intermediate positions during the rotation (one rotation or less), which should otherwise be partial connection preventing left-hand rotation, which provides a step-load-bearing threads 20 and the selected height of the hooks 44 of the latch./p>

It should now be clear that the architecture with three jaw clutches and fixation of the present invention is well suited to the creation of an additional radial stroke, which may be preferable from an external exciting tools such as shown in Fig. 1, where, for example, it is usually necessary to capture the United tubular products in the size range below the coupling.

Architecture with three jaw clutches exciting inside (internal grip) instrument descent tubular products

In Fig. 8-13B shown below, the preferred implementation of the improved gripping tool, called in this document "an instrument descent tubular products with internal capture architecture with three jaw clutches". In Fig. 8 shows the appearance of the instrument descent tubular products preferred variant implementation, in General, indicated by position 100 and shows how it should look in a configuration latch having a layout 110 of the housing and the arrangement 120 of the capture element.

In Fig. 9 shows a sectional view of the tool 100 of descent tubular products, how should it look like in configuration with the latch on the inside and installed on the same radius with the middle end 101 of the product 102. The tool 100 of the descent tube isdel the th made at the upper end 105 for connection with the hollow shaft of the top drive, or lower end of the column drive component, to which is attached (not shown) carrying the load adapter 112, a built-in spindle 130 so that the spindle 130 acts as the main body of the tool 100 of descent. Carrying load the adapter 112 is, in General, axisymmetric and made of a material of suitable strength. He has an upper end 121 made with internal thread 122, suitable for airtight connection with the hollow shaft of the top drive with an internal pass-through channel 123, continuing channel of the spindle 130.

Also shown on Fig. 9 the tool 100 descent tubular products has a layout 110 of the housing consisting of an elongated, generally cylindrical spindle 130 having an upper end 131, the lower end 132 with the outer surface 133 in the form of a truncated cone, and the inner channel 136. The spindle 130 134 is threaded on the housing and splined element 135 at the upper end 131. The tool 100 descent tubular products supplied retaining ring 140 having a splined section 142 at the lower end 141. The retaining ring 140 is shown here have, in General, a tubular outer sleeve 184, outside carrying a load adapter 112, and firmly attached to it, where the outer sleeve 184 is designed to protect the bearing load of the adapter 112 from damage to the pipe key. The spindle 130 carries an internal axially include the Yu in work arrangement 120 capture, having an elongated and generally cylindrical lower end 109, inserted in the upper middle end of the pipe 101 articles 102 and is coaxially placed in it. The arrangement 120 of the gripper consists of a casing 144, with the upper end 145 and the lower end 146 having a threaded element 147 at the lower end 146, the axial retaining groove 148 and a multitude of radially oriented Windows 149, placed around the circumference at the lower end 146, which are jaw 160. In General, extra long jaws 160, with the upper end 161, a lower end 162, the inner surface 163, the outer engagement surface 164 and parallel sides (not shown), have a lot of contact faces 166 in the form of a truncated cone on the inner surface 163 connecting abutting with them surfaces 133 in the form of a truncated cone spindle 130, forming a junction 114 V-capture acting for radial stroke of the jaws 160 in response to axial actuation.

As also shown in Fig. 9, the tool 100 descent tubular products has dukhobortsy mechanism 200 control actuation axial passage with three jaw clutches with detent, in General, performed architecture with three jaw clutches, and includes a leading Cam clutch 220, the driven Cam clutch 260 and the intermediate Cam clutch 240. Fur is ISM 200 control acts between the spindle 130 and layout 120 capture and consists of a link 180 of the housing, includes master and slave Cam housings 181 and 182, respectively. The mechanism 200 control with three jaw clutches with detent operates and is arranged, in General, as described above and shown in the diagrams of Fig. 3-4C and 6A-6C.

In Fig. 10A shows the mechanism 200 management in configuration with the latch arrangement which is equipped with the leading Cam sleeve 220 with the upper end 222. As shown in Fig. 10B in the form of a cross-section of the layout 200 with three jaw clutches in configuration with the latch arrangement 200 with three jaw clutches has a leading Cam sleeve 220 with the lower end 223, the outer surface 224 and the inner surface 225, and one or more protrusions 226 transfer torque (here eight) at the upper end 222. The inner surface 225 of the leading clutch 220 has a threaded element 227 on the upper end 222 and the sealing element 228 at the lower end 223. As also shown in Fig. 9, the threads 134 of the housing on the spindle 130 sbencivu with the screw element 227 at the leading Cam sleeve 220 and the sealing element 228 is hermetically connected to the outer surface of the spindle 130. Slotted section 142 of the retaining ring 140 engages with the notches of the transfer of torque (not visible in this section, but are shown in Fig. 10B position 226) at the leading Cam sleeve 220, and with the slotted element 35 on the spindle 130 so the host Cam sleeve 220 structurally and rigidly attached to the spindle 130 and prevented its movement, as axial and circumferentially relative to the spindle 130. As also shown in Fig. 10B, the lower side 229 of the leading clutch 220 contains duplicate the hooks latch 230. The outer surface 224 of the leading clutch 220 contains a variety of load-bearing threads 231 at the lower end 223. Bearing the load of the threads 231, in General, consist of buttress threads with load-bearing side of the 233 thread profile and guide the side 234 of the thread profile. The leading Cam sleeve 220 has a sealing element 236 on the outer surface 224 at the upper end 222. As also shown in Fig. 10A, the leading Cam sleeve 220 has a surface 232 stops and surface 237 of inclined lugs placed on facing down the outer surface 224 of the ledge 296 on the upper end 222.

As also shown in Fig. 10A, the intermediate Cam sleeve 240 with the upper end 241, a lower end 242, the inner surface (not shown) and the outer surface 244 has one or more surfaces 245 stops (shown here) at the upper end 241 connecting surfaces 232 stops at the upper end 222 of the leading clutch 220, together forming a pair of 255 surfaces of the stops. Also on the upper end 241 of the intermediate Kula is a similar clutch 240 are one or more (shown as three) surfaces 256 of inclined lugs, which couple a sliding connection with surfaces 237 inclined lugs leading clutch 220, together forming a pair 257 surfaces sloping lugs. As also shown in Fig. 10B, the intermediate Cam clutch 240 is perceiving the load thread 246 (shown here as a form of multiple threads with pitch matching step helix surfaces 256 of inclined lugs) on the inner surface 243 on the upper end 241, and the data thread is designed as a pusher thread with load-bearing side 247 of the thread profile and the guide side 248 of the thread profile and joined a sliding connection with the load-bearing thread 231 of the leading clutch 220, forming the bearing load screw a couple 268 and thus, together with a pair of 255 surfaces of the lugs and a pair of 257 surfaces inclined stops, together forming the leading couple 249 clutch 249. In Fig. 10A intermediate Cam sleeve 240 has one or more (here six) helical surfaces 250 of load-bearing inclined sections placed adjacent to or equal to the number of load-bearing surfaces 251 stops and on the same radius with them, at the lower end 242.

As also shown in Fig. 10A, led Cam coupler 260 to the upper end 261, the lower end 262 and the outer surface is Yu 263 has many helical load-bearing surfaces 265 sloping ground, placed adjacent to the surfaces 266 stops perceiving the load and on the same radius with them at the upper end 261. Helical surface 265 of inclined sections, load-bearing, and surface 266 stops, the load-bearing, slave clutch 260 are joined by a sliding connection with the helical surfaces 250 sloping ground, the load-bearing and surfaces 251 stops, the load-bearing, intermediate clutch 240, together forming the driven Cam couple 267. As shown in Fig. 10B, led Cam sleeve 260 has one or more protrusions 269 torque transmission, in this case twelve (12), on the bottom side 270 at the lower end 262. As shown in Fig. 9, the protrusions 269 transfer torque driven clutch 260 is connected with protrusions 143 of the transmission torque at the upper end 145 of the casing 144 in this embodiment, are connected together by bolts in holes 297 under the bolts (bolts not shown) for structural and rigid connection slave clutch 260 with a casing 144. As also shown in Fig. 10B, on the inner surface 264 on the lower end 262 of the driven clutch 260 has a sealing element 273 and turned up the ledge 274, and on the outer surface 263 at the lower end 262 has a sealing element 275.

As also shown in Fig. 10B layout 200 of Cam clutches has in General, in the form of tubular goods, the ring 300 of the latch with the upper end 301, the lower end 302, and the inner surface 303. In Fig. 11 shows the layout of the leading clutch 220, the ring 300 lock and key 290 retainer ring 300 retainer has a lot of screw jacks 305 dowels release (here six), which can be evenly spaced around the circumference on the outer surface 304. Socket 305 clamps clamps have an inner edge 306, bearing faces 307, and helical faces 309 and 310 of the sliding Cam. The inner face 306 of the slot 305 of the key lock has a groove 308 of free space under the pin, passing to the inner surface 303 of the ring 300 retainer. As also shown in Fig. 10B, at the lower end ring 302 300 retainer on the inner surface 303 has turned up the ledge 315. The top side 312 at the upper end 301 of the Cam ring 300 retainer has a duplicate hooks latch 313. Hooks 313 of the latch on the Cam ring 300 retainer are joined with hooks 230 of the latch on the underside 229 leading clutch 220, together forming a pair of hooks 314 of the latch hooks 230 and latch 313 is chosen so that when you connect a pair of hooks 314 latch prevents relative axial movement of the driven clutch 260 and leading clutch 220.

As also shown in Fig. 11A,the ring 300 retainer combine what pins latch 290 is placed inside the slots 305 key lock. In Fig. 11B shows, partially in section, view of part of the Assembly with the jaw clutches, which includes the slave Cam ring 260, the ring 300 of the latch pins 337 clamps, pins 290 of the latch and the spring elements 346 and 349, pins 337 lock and lugs 338 clamp (not shown in this view) is rigidly attached to the drive Cam sleeve 260 and pass through the Cam sleeve for sliding connection with the holes 291 under shear pins in pins 290 of the latch. As shown in 10A, radially oriented pin 337 clamp in Association with radially oriented eye 338 of the latch, which is not aligned in a radial plane with the pin 337 clamp together restrict the movement of the pins 290 of the latch relative to the driven clutch 260 so that the movement of the ring 300 of the latch is limited to helical movement relative to the driven clutch 260 on the value formed by the relative difference in axial length between, as shown in Fig. 11A, housing 290 of the latch and the slot 305 of the key retainer. Also, as shown in Fig. 11B, the pins 337 latch with the inner ends 339 ejected through the slot 308 of free space in the socket 305 key lock, and ov are connected with the holes 323 under the pins uderjivaya what about the ring in the retaining ring 320 and together limit the movement of the retaining ring 320 relative to the driven Cam ring 260. Also, as shown in Fig. 11A arranged in bearing the load faces 293 pins 290 lock and load bearing faces 307 ring 300 lock together form a pair of 315 load-bearing faces, if the retainer axial load is transmitted from the driven clutch 220 (not visible in this view) on the ring 300 release a couple 315 load-bearing faces. Spiral moving Kulakova face 296 and 297 of pins 290 latch and helical Cam faces 309 and 310 of the ring 300 lock together to form pairs 317 and 318 spiral sliding Cam faces, respectively, so that when the pins 290 latch is moved up or down relative to the ring 300 retainer, pair 317 or 318 of Cam faces, respectively, are connected. In Fig. 11C shows part of the layout, which includes a leading Cam clutch 220, the ring 300 lock and key 290 of the latch, as it should look when the initial right-hand rotation of the leading clutch 220, the ring 300 of the latch is pushed down to the position shown, where the hooks 314 have a small overlap 316 for the implementation of re-fixation under the action of left rotation, as shown in Fig. 6B and described above, but do not interfere under the action of the subsequent right rotation to cause axial stroke, limited movement along the load-bearing threads 231. So is e, as shown in Fig. 10B, the arrangement 200 with three jaw clutches may be of the spring element 346, in this case, the spiral spring placed inside the ring 300 retainer and working in compression between the retaining spring ring 320 and ring 300 of the latch, so that the spring element 346 usually works in conjunction with gravity and functions, deflecting ring 300 retainer in axial lower position.

Also, as shown in Fig. 9, the arrangement 200 with three jaw clutches inside the layout 180 the Cam casing consisting of a casing 181 driven clutch rigidly attached to the driven Cam sleeve 260 and hermetically connected to the sealing element 275, and a casing 182 leading clutch, rigidly attached to the leading Cam sleeve 220 and hermetically connected to the sealing element 236, and the layout 180 shroud create a sealed chamber 183 of the Cam clutch adds a compressed gas into the chamber 183, functioning as a spring tending to draw the layout 122 capture in connection with the product 102 after disconnecting latch 295.

In Fig. 10A on the appearance of the layout 200 with three jaw clutches shown should look like arrangement in a fixed position, where the leading Cam sleeve 220, driven Cam clutch 260 have a minimum the initial axial spacing, so the leading Cam pair (not shown), a pair of 255 surfaces of the lugs and a pair of 257 surfaces inclined lugs leading and intermediate Cam clutches 220 and 240, respectively, are connected to, and driven Cam pair 267 intermediate and driven Cam clutches 240 and 260, respectively, are connected. In Fig. 10B shows a sectional view of the link 10 with three jaw clutches in the configuration latch is equipped with a ring 300 of the latch, the latch 295 which is placed within and on the same radius with the arrangement 200 with three jaw clutches described above and shown in Fig. 6A-6C. The latch 295 creates a means to prevent free axial cultivation leading and the trailing Cam clutches 220 and 260, respectively.

In Fig. 12A shows the appearance of the layout 200 with three jaw clutches, how it should look with the application of the right of torque, the leading Cam couple 249 concatenated and leading Cam sleeve 220 was two thirds of a turn relative to the driven clutch 260 and the intermediate clutch 240. Bearing the load of a pair of surfaces 268 stops and driven Cam pair 267 are in engagement, reacting as axial and torsional load between the guest and the intermediate jaw clutches 260 and 240, respectively. In Fig. 12B shows a sectional view of the layout 200 with three jaw couplings is, how it should look with the application of the right torque, as described above and shown in Fig. 12A. The latch 295 disconnected and ring 300 of the latch is in the down position, displaced by the force of gravity (in this orientation) and a spring element 346 so that the lower portion 302 of the ring 300 of the latch is connected to a spring element 349. The spring element 349 is a relatively stiff spring, in this embodiment, a stack of Belleville springs, consisting of three Belleville springs arranged in parallel and pre-compressed so that the combined force of deflecting elements acting on the ring 300 retainer, small relative to the pre-loading of the spring element 349 and, therefore, the position of the spring element 349 is known and, therefore, the axial position shifted down ring 300 of the latch is also known. The spring element 349 operates to prevent excessive loading hooks 314 of the latch when the compressive load is applied to the arrangement 200 with three jaw clutches only limited by a pair of hooks 314 of the clamp connection. Left spiral leading Cam pair 255, in this case in the form of American resistant trapezoid thread with six visits, provides the rotation causing axial stroke exceeding one paragraph is LEGO rotation, which is more than possible with a single Cam pair bilateral rotation described above and shown in Fig. 2A and 2B.

In Fig. 13A shows the appearance of the layout 200 with three jaw clutches, how it should look with detached lock 295 and under the influence of the application of the left torque, driven Cam pair 267 is connected, and the leading and intermediate Cam clutch 220 and 240, respectively, were relatively small rotation relative to the driven clutch 260. Pair 255 surfaces of the lugs and a pair of helical surfaces inclined lugs 257 are connecting to respond to axial and torsional loads between the leading Cam sleeve 220 and the intermediate Cam clutch 240. In Fig. 13B shows a sectional view of the layout 200 with three jaw clutches, how it should look with detached lock 295 in the case of application of the left torque ring 300 of the clamp is drawn down so that the lower part of the ring 302 300 retainer is in contact with the spring element 349. To move a layout 200 with three jaw clutches of fixed configuration described above and shown in Fig. 9A and 9B, in the configuration shown in Fig. 13A and 12B, it is necessary first to apply the right torque for ataegina latch 295, then applying axial offset is e, sufficient to move the hooks 314 of the latch beyond the overlapping (see Fig. 11B), so that under the action of applied left torque driven Cam pair 267 should connect without interference from the hooks 314 of the latch. As also shown in Fig. 9, axial stroke required to move the hooks 314 of the latch beyond the connection made with the possibility of getting into the play of the tool, i.e. axial stroke required before a possible connection link 120 engagement with product 102. Right helical driven Cam pair 267, in this case hestitantly sloping plot, creates axial stroke and torsional load application left rotation angle of the intermediate clutch and also creates free axial breeding intermediate and driven Cam clutches 240 and 260, respectively, if the latch 295 disconnected, providing axial stroke exciting tool 100 to capture product 102 under the applied axial load, independent of the rotation.

In this patent document, the word "comprising" is used in a non-limiting sense, meaning that items following the word are included in, but not specifically mentioned are not excluded. The reference to the element with an indefinite article "a" does not exclude the possibility of the presence of som is of such elements, if the context clearly requires having one and only one element.

Specialist in the art it should be clear that it is possible to perform modifications to the shown embodiments without departing from the essence and scope of the invention, as defined below in this document in the claims.

1. An improved gripping tool having a gripping surface, which are movable gripping elements, and the control mechanisms for radial movement of the surface of the capture of venutolo in the extended position, comprising: a management mechanisms that contains at least one control mechanism with three jaw clutches, comprising: a lead Cam coupler receiving an input rotation, aspiring to transfer rotation; intermediate Cam coupler receiving an input rotation exclusively from the master clutch; the driven Cam coupler receiving an input rotation solely from the intermediate clutch; a leading Cam couple acting between the leading Cam clutch and the intermediate Cam coupling so that the input rotation is transmitted to the leading Cam couple from leading clutch on the intermediate Cam clutch and the driven Cam pair, acting between the intermediate Cam clutch and driven Cam m is ftoi so, the input rotation from the intermediate clutch is transmitted to the driven Cam pair on the driven Cam clutch.

2. The tool according to claim 1, in which the control mechanism with three jaw clutches provides dvuhoborotny control axial passage and a radial passage surface of the gripper tool as a function of axial travel.

3. The tool according to claim 2, in which the leading Cam pair is made with the possibility of causing only axial stroke as a function of the rotation in the first direction of rotation and driven Cam pair under the action of the second direction of rotation, the separation dogovornogo control two Cam pairs leads to the establishment of greater axial stroke and correlative radial traverse the surface of the grip, which is possible when using a single pair of Cam, when dvuhoborotnym the control mechanism.

4. The tool according to claim 1, in which the control mechanism with three jaw clutches are made with a latch which, when the connection prevents actuation of the axial stroke of the control mechanism with three jaw clutches.

5. The tool according to claim 4, in which the control mechanism with three jaw clutches is provided with a mechanical lock, which when included in the work prevents the connection of the latch.

6. The tool is NT according to claim 1, a captivating instrument has a load bearing adapter, and a control mechanism with three jaw clutches is located so that the leading Cam clutch is rigidly fixed to the load bearing adapter and receives the input rotation, aspiring to transfer the rotation.

7. The tool according to claim 6, in which the control mechanism with three jaw clutches provides dvuhoborotny control axial passage and a radial passage surface capture as a function of axial travel.

8. The tool according to claim 6, in which the leading Cam pair is made with only causing axial stroke as a function of the rotation in the first direction of rotation and driven Cam pair under the action of the second direction of rotation, the separation dogovornogo control two Cam pairs leads to the establishment of greater axial stroke and correlative radial traverse the surface of the grip, which is possible when using a single Cam pair in dvuhoborotnym the control mechanism.

9. The tool according to claim 6, in which the control mechanism with three jaw clutches are made with a latch which, when the connection prevents actuation of the axial stroke of the control mechanism with three jaw clutches.

10. The tool according to claim 9, in which the control mechanism t is EMA jaw clutches is provided with a mechanical lock, which, with the inclusion of the work prevents the connection of the retainer.



 

Same patents:

FIELD: machine building.

SUBSTANCE: required values of detachment pressure are determined on the basis of rod size and/or pipe dog type. The upper and lower limits for permissible values of rod detachment pressure may be calculated on the basis of the required pressure of detachment and/or rod size. Values of rod detachment pressure below the lower limit and above the upper limit specify the necessity to analyse the rod condition in order to identify whether this rod may be used repeatedly. The values of rod detachment pressure may be recorded as data of detachment pressure for subsequent assessment, including detection of improper unscrewing of rods and poor condition of a well.

EFFECT: invention provides for identification of pipes that require replacement.

25 cl, 13 dwg

FIELD: machine building.

SUBSTANCE: top drive comprises gripping device jointed thereto and arranged there under, and four grippers each being arranged on piston with gripping cylinder. Proposed method of pipe gripping above top drive comprises activating pistons and cylinders of above said device. Invention covers also top drive with drive shaft, component coupled with said shaft and gripping device with mouth suspended to top drive and provided with first splined element. Note here that said component has second splined element for engagement with first splined element to selectively decelerate component rotation for unlocking the joint with top drive driving shaft. Note also that gripper comprises two parts that move for opening the mouth. Proposed method comprises engaging said second splined element and decelerating component rotation for unlocking the joint.

EFFECT: normal operation of top drive, easier installation, smaller installation space.

30 cl, 6 dwg

FIELD: oil and gas production.

SUBSTANCE: heat breaker consists of base member and of steam generator. The latter has a handle connected to a case with bushings and screws. In the case there is installed a container consisting of a tubular electric heater, of heat carriers and of a shedding screen. Also, heat-insulating material and shutters equipped with the heat screen and movably connected to the case by means of loop are positioned between the case and the container. A mechanism of shutters opening consists of ears, a cable, a lever and springs closing the shutters. A mechanism of fluid supply to the heat carrier corresponds to a compartment with a removable cover wherein there is arranged a spring loaded tube with a valve, while a cover-stop is set above the container with screws.

EFFECT: reduced stress in threaded connections of pipes before their unscrewing, enhanced efficiency of threaded connections in oil pipes; upgraded quality and reliability of threaded connections during pipe unscrewing; increased service life of pipes.

6 dwg

FIELD: process engineering.

SUBSTANCE: invention relates to automation of pipe running and pulling in oil extraction. Proposed device comprises drilling data base that stores records about pipe elements, controlled-torque wrench with rotation drive, and controller. In screwing off, controller detects records in drilling data base on type of pipe elements to allow wrench torque control or that of rotary device to connect additional pipe section to pipe casing, or to screw off joint between pipe elements in compliance with parametres of given pipe elements joint. Various components of drilling unit incorporate transducers, magnitudes transmitted by said transducers being controlled. Simultaneously with screwing off/on jobs, timers are initiated. When magnitudes red by transducers fall beyond preset range, or when performance of aforesaid jobs last too long to completion, emergent situations originate.

EFFECT: acceleration of jobs at drilling site.

26 cl, 3 dwg

FIELD: oil and gas industry.

SUBSTANCE: wrench with adjustable torque moment for pipe elements includes lower and upper grips, pivot bearing located between grips, actuation system connected between grips and system for measurement of actual radius or system for measurement of actual vector of force created with actuation system. At that, pivot bearing provides the possibility of turning upper and lower grips relative to each other by means of actuation system. Measurement method of torque moment at bringing the wrench into operation involves measurement of actual radius measured perpendicular to force vector and between force vector and rotation axis of pipe element, or measurement of actual force which is applied for action of torque moment on the connection, and calculation of torque moment on the basis of at least one measurement.

EFFECT: increasing operating efficiency of spinning wrench.

12 cl, 6 dwg

FIELD: transport.

SUBSTANCE: device for moving, connecting and disconnecting pipe section with pipe column contains pipe engagement assembly made capable to be connected with driving shaft of upper drive to transfer torque during pipe section spinning up/down. Herewith, pipe engagement assembly has self-engaging ball and cone assembly made capable to engage with pipe section. Ball and cone assembly is resistive to both static and dynamic load and is configured to carry total weight of pipe column during simultaneous rotation and vertical movement of the pipe column in a well. Pipe engagement assembly may be made interchangeable with internal or external pipe section gripper with power disengager controlled by hydraulic or pneumatic system, and with locking mechanism. Ball and cone assembly contains multiple balls with at least one direction inside multiple cones; herewith, multiple cones are oriented in at least two different directions. The claim also includes methods for engagement and disengagement of pipe section with pipe column using the said device.

EFFECT: reduced labour input for round trip operations.

28 cl, 8 dwg

FIELD: gas-and-oil industry.

SUBSTANCE: hydraulic key for starting screw of drilling column consists of two successively installed sections: first one hinged on bracket of drill tower and second one with fixed jaw, of movable jaw, of rocking arm, of hydro-cylinders for supply, lock, and start and of limit switch installed between bracket and first section. The first section has a slot wherein a centre pin of the second section enters. One lever of the rocking arm is pivotally connected to the movable jaw, its central part is connected to the second section, while the lock hydro-cylinder is positioned on the second lever of the rocking arm coupling it with the second section. The hydro-cylinder of supply is arranged on the drill tower and the first section; the hydro-cylinder of start is positioned on the first and second sections. Also the hydraulic key is equipped with an additional limit switch installed between the first and the second sections. Axis of the hydro-cylinder of start forms angle 45÷90° with a straight line passing through contact points of the jaw of the second section with the drilling column; also points of fixture of the hydro-cylinder of start on the first section and points of fixture of the first section on the bracket coincide.

EFFECT: increased reliability and automatic control of hydraulic key operation.

2 cl, 1 dwg

FIELD: machine building.

SUBSTANCE: drive, rotating chuck kinematically tied with drive, and unit of fixation and axial feed of pump rod are mounted on foundation. The rotating chuck corresponds to end flanges coaxially arranged and rigidly tied, and to two rings installed between the flanges; the chuck is inserted between rings of a separator. The separator is equipped with offset cams arranged on axes and has slots and lugs correspondingly interacting with lugs and recesses of the cams.

EFFECT: expanded process functionality and arsenal of stationary tools for tube bases and repair shops of oil industry enterprises.

3 cl, 4 dwg

FIELD: oil and gas production.

SUBSTANCE: round-trip device comprises oil-well tubing, a pipe wrench pipe wrenchand a spider accommodating elements provided with both hardened profiled, and the smooth unhardened surfaces to interact. The invention provides designing of the hardened profiled elements on external surface patches of the oil-well tubing within interface with the oil-well tubing and spider which are provided by the elements with the smooth unhardened surfaces.

EFFECT: higher reliability of the current equipment by decreasing the probability of parting and dropping the various fragments of the round-trip device.

FIELD: oil and gas production.

SUBSTANCE: fixing mechanism includes a pair of clamping jaws, rods and hydraulic cylinder as drive, which are connected to them. At that, mechanism also includes the lever installed with possibility of being turned, longitudinal rod and reverse lever. At that, hydraulic cylinder is connected to the lever, one end of which is connected to rod connected to the first clamping jaw, and its other end is connected by means of longitudinal rod to reverse lever connected by means of rod to the second clamping jaw.

EFFECT: improving operating reliability and reducing the cost owing to simplified device design.

2 dwg

FIELD: oil and gas production.

SUBSTANCE: device for transfer of tubular element consists of component with multitude of elongated slots, of component with multitude of recesses connected with components with slots and designed to slide, of multitude of rolling elements each retained between one of recesses and one of slots, and of multitude of shift components each shifting corresponding rolling element. The procedure for shifting the tubular element consists in introduction of the above described device into an end of the tubular element, in creating conditions for engagement of multitude of rolling elements between surfaces of the tubular element and the component with recesses and in lifting the tubular element by means of the above described device. The system for transfer of the tubular element contains the above described device and means for lifting the described device for transfer of the tubular element.

EFFECT: safety, efficiency, low expenditures, and possibility to operate with pipes of different dimension.

14 cl, 9 dwg

The invention relates to deep drilling, in particular, is a wedge device for gripping pipes tackle system

The invention relates to deep drilling, in particular, is a wedge device for gripping pipes tackle system

FIELD: oil and gas production.

SUBSTANCE: device for transfer of tubular element consists of component with multitude of elongated slots, of component with multitude of recesses connected with components with slots and designed to slide, of multitude of rolling elements each retained between one of recesses and one of slots, and of multitude of shift components each shifting corresponding rolling element. The procedure for shifting the tubular element consists in introduction of the above described device into an end of the tubular element, in creating conditions for engagement of multitude of rolling elements between surfaces of the tubular element and the component with recesses and in lifting the tubular element by means of the above described device. The system for transfer of the tubular element contains the above described device and means for lifting the described device for transfer of the tubular element.

EFFECT: safety, efficiency, low expenditures, and possibility to operate with pipes of different dimension.

14 cl, 9 dwg

FIELD: machine building.

SUBSTANCE: invention refers to tubular products gripping and manipulation tool. Gripping tool has gripping surface that is borne against movable gripping elements and control mechanisms for radial movement of the gripping surface from retracted to extended position. Gripping tool includes control mechanisms comprising at least one control mechanism with three cam clutches, which in its turn includes drive cam clutch receiving the input rotation and tending to the rotation transfer; intermediate cam clutch receiving the input rotation only from drive cam clutch; driven cam clutch receiving the input rotation only from intermediate cam clutch; drive cam pair acting between drive cam clutch and intermediate cam clutch so that input rotation is transmitted by drive cam pair from drive cam clutch to intermediate cam clutch, and driven cam pair acting between intermediate cam clutch and driven cam clutch so that input rotation from intermediate cam clutch is transferred by driven cam pair to driven cam clutch.

EFFECT: providing the control of axial and radial movements of gripping tool surface.

10 cl, 13 dwg

FIELD: oil-and-gas industry.

SUBSTANCE: invention relates to handling tube elements in drilling the wells. Tube handling tool comprises preloading element to apply axial force and actuating mechanism to produce axial force, tool coupler to engage actuating mechanism with tube handling tool, and tube coupler to transfer axial force produced by actuating mechanism, slotted element with multiple long slots extending in some direction, element with recesses articulated with slotted element and having multiple recesses each tapered in direction from shallow end to deep end, and multiple rolling elements each extending through one of said slots provided location in shallow end of one of said multiple slots, and pulled inside slotted element provided location in deep end. Note here that, at least, portion of axial force is transferred via tube element to, at least portion of multiple rolling elements.

EFFECT: reliable operation, proper joint with tubes.

16 cl, 7 dwg

FIELD: drilling oil and gas wells; devices for screwing and unscrewing casing pipes.

SUBSTANCE: proposed wrench includes power unit in form of electric motor, hydraulic pump with constant power regulator and tank filled with working medium. Actuating mechanism includes hydraulic motor, gearbox, rotor with pipe grip, movable doors with locks and hydraulic distributor. Constant power regulator is provided with delay unit in form of prestressed spring. Axial-flow piston-type pump is used as hydraulic pump; it is provided with movable unit with spring and its pistons are arranged in inclined position. Constant power regulator inlet is connected with main hydraulic line and its outlet is connected with cylindrical movable unit of hydraulic pump. Constant power regulator may be switched-off by delay unit. Regulator is switched on when output power of power unit and output of hydraulic pump reach the magnitudes preset by the following formulae: where N, are respectively output power and normal output power of power unit; Q are respectively output and nominal output of hydraulic pump; P are respectively pressure and nominal pressure of working medium in hydraulic line, k is proportionality factor equal to 1.

EFFECT: enhanced efficiency, reduced wear; increased universality factor.

4 dwg

FIELD: drilling equipment, particularly devices adapted to lower and lift drill string.

SUBSTANCE: device includes connection parts formed on drilling pipe sections, for instance as sleeve or male half of tool joint with tool-joint threads, rotary key for above members and supplementary means. Supplementary means have cavities with sensors and is built in drilling string. The means are also provided with detachable reinforcing clamp made as bails connected one to another. The bails are arch-shaped and plate-type and are pivotally connected one to another. Inner bail surfaces have extensions inserted in grooves formed in supplementary means so that groove dimensions correspond to that of bail extensions.

EFFECT: reduced size of lock connection and increased free space for measuring tools installation.

3 cl, 4 dwg

FIELD: mechanical engineering, particularly connecting or disconnecting drilling and casing pipe couplings or joints.

SUBSTANCE: key is divided into separate independent technological units and has upper and lower bodies with connectors in front parts thereof. Built in the front parts are toothed rotor wheels in which pipe clamping means are arranged. The key also has gear and intermediate gear assemblies, common drive to rotate and stop the pipes. The drive comprises differential and high-speed reduction gears with hydraulic motors. Upper body may be rotated about pipe clamping means axis to lift or lower thereof relative lower body. The body is provided with thread torqueing/loosening means, braking means and means to supply process lubricant to threaded nipple part of pipe to be screwed on. Lower body has thread torqueing/loosening means. The key also comprises positioner provided with horizontal and vertical key displacement mechanisms.

EFFECT: extended functional capabilities, reduced time to replace clamping members of upper and lower key executive tools and braking system members, increased reliability of device units, increased load-bearing capacity of pipe interlocks.

3 cl, 6 dwg

FIELD: mechanical engineering, particularly connecting or disconnecting pipe couplings or joints, spinning wrenches adapted to connect drilling and casing pipes.

SUBSTANCE: device comprises rotary gear with connector provided with pentahedral profile from inner side thereof and cartridge built in the pentahedral profile. The cartridge has upper and lower discs with four clamping means arranged between them in radial direction. The clamping means are made as shuttle mechanisms comprising bodies and jaws with hard-alloy dies. The bodies are built in guiding cartridges and may perform radial movement during rotary gear rotation. Movable pins are built in clamping device body. Projected pin ends mate projections made in cups. The cups are arranged between cartridge discs and provided with spring. Jaw with die is connected with the body by pin so that after pin disconnection the body may be removed from the guiding cartridge.

EFFECT: increased reliability along with increased load-bearing capacity.

2 cl, 3 dwg

FIELD: mechanical engineering, particularly drilling string and casing pipe connection equipment.

SUBSTANCE: method involves stopping one pipe and rotating another pipe for screwing and unscrewing of above pipes with the use of hydraulic drive and braking system to transmit differently directed torques with the same data along with reactive moment reduction by drive and braking system. Device comprises two coaxial power tongs. Each power tong includes body and pipe squeezing mechanism. The power tongs have common drive including high-speed reducer and differential block kinematically connected one to another. Differential block comprises body with outer and inner toothed crowns, planet carrier with three satellites installed on the carrier, the first tong arranged in body, driven gear kinematically connected to planet carrier and the second tong installed in the body and adapted to cooperate with corresponding gears of pipe squeezing mechanisms. Pipe squeezing mechanism of the first tong is fixedly secured to braking pulley of braking system installed on the first tong body. The braking system comprises four pressing shoes and cylindrical case with hydraulic cylinder for shoe pressing arranged so that cylindrical case may rotate with pulley and pipe squeezing mechanism of the first tong relative pipe squeezing mechanism axis. The cylindrical case is additionally provided with two rests. One rest is fixedly connected with cylindrical case and cooperates with two hydraulic cylinders, which are adapted for thread tightening/unfastening. Another rest is connected with cylindrical case by hinged axis and also cooperates with two other hydraulic cylinders, adapted for thread tightening/unfastening, which provides elimination of reverse reaction and increase of pipe squeezing mechanism torque and locking moment.

EFFECT: possibility to use one drive provided with differential gear to perform screwing/unscrewing operations.

2 cl, 2 dwg

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