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

This invention relates preferably to such applications where the need to capture the tubulars and the tubular string, the manipulation and lifting tool connected rotator drilling rig or structure of the application reactive forces for transmission of both axial and torsional loads on the grip tube section or from her. In the land drilling, well construction and servicing by drilling rigs and workover of wells, this invention relates to slips, and more specifically, on rigs using top drives, applies to tools lowering tubulars, attached to the top drive for capture close to his section of the tubing string, increases in the wellbore, deployed it or learn from it. Such instruments lowering tubulars are various functions necessary or beneficial to these operations including a quick coupling and release, upgrade, indentation, rotation and flow of fluid under pressure in the tubular string and release therefrom. According to the invention set up control mechanisms to enhance or improve the range of capture tools such descent tubulars.

Until recently, mechanical tongs established method used for lowering casing or drill pipes in oil wells and recovery from the wells in conjunction with the drilling rig hoisting system. This method using a mechanical tong provides a relatively efficient assembly of pipe strings, comprised of pipe sections or parts of the joints threaded ends by screwing the mating threaded ends (bonding) to form threaded connections between sequential pipe sections with their capacity for the column set in the wellbore; or reverse the process of recovery and removal (unfastening). However, this method using a mechanical tong simultaneously carries other useful functions, such as rotation, indentation or filling fluid, after extension of the pipe section at the column or its removal from the column, and during the descent or the rise of the column in the wellbore. Descent tubulars using tongs and usually requires staff in high-risk areas, such as the drill floor or even dangerous, above the drill floor, the so-called 'balconies to work with the casing. "

The appearance of rig equipped with a top drive gave a new method of descent tubulars and, specifically, the casing, where the top drive is equipped with a so-called 'tool descent tubulars top drive' to capture and, if possible, create a seal between the short section of pipe and hollow top drive shaft. (It should be understood that the hollow shaft of the top drive generally incorporates components such actuator column, which can be attached thereto, the distal ends of which effectively acts as an extension of the hollow shaft). Therefore, we developed various devices, generally designed for perform 'running casing top drive'. Using these devices in coordination with the top drive allows lifting, rotating, indentation and filling a casing string the drilling fluid during the descent, thus eliminating limitations associated with using mechanical tong. Simultaneously, automation of the gripping mechanism in association with the specific advantages of the top drive reduces the degree of involvement of the personnel required in comparison with the descent using mechanical tong and thus improves safety.

In addition, when handling the casing and the descent using a tool shutter tubulars using a top drive string weight must be transferred from the top drive to a support device when the nearby box or the section of pipe or build up was removed from the collected column. This function typically performs 'annular wedge grip' powered by an axial load gripping device that uses 'slips' or jaws placed in having a hollow 'body slips' through which descend the casing where casing slips has a channel-shaped frustoconical with downward decreasing diameter and is supported on the rig floor or mounted in the drill floor. Slips acting as annular wedges between the pipe section at the proximal end of the column and the inner surface of the frustoconical body slips, with the application of traction load grips the pipe, but moves out or slip downward and thus radially inward on the inner surface of the casing slips when the weight of the column moved to grip. The radial force between the slips and pipe body is thus 'automatically created' or 'automatically turns' axial load, ie, when considering the traction ability of the dependent variable and the column weights of the independent variable, there is a control loop with positive feedback, wherein independent variable weight column rigidly piped to the feedback controlling the radial gripping force which acts monotone, driving ability or traction slip resistance, is the dependent variable. Similarly, the opposition should be torque fastening and unfastening annexed to located in the section of the pipe at the near end of the collected column. This function is usually performed tong having jaws connecting to the nearest section of the tube and a lever attached coupling member, such as a chain or cable, to the construction of the rig to prevent rotation and, thus, creating a resisting torque unreacted wedge grips in casing slips. Gripping force of tongs are usually similar to 'automatically creates' or 'is automatically switched' positive feedback of the applied load torque.

In general, the pick-up tool PCT patent application CA 2006/00710 and US application 11 / 912.665 can be described as pick-up tool, comprising a housing arrangement having a carrying load adapter coupled for axial load transfer to the remainder of the housing, or, in short, the basic housing, wherein the load bearing coupler configured to constructive compound rotator machine or frame transmission reactive forces exciting arrangement which carries a main body having a gripping surface, the gripping arrangement equipped with a means of setting into operation to radially stroke or move from a retracted position in the coupling position for the radial load compounds traction or gripping surface to the inner surface or the outer surface of the article in response to relative axial movement or axial stroke of the main body, at least in one direction relative to the gripping surface. A mechanism control operating between the arrangement enclosure and the exciting arrangement which, when rotated, at least in one direction of the load bearing adapter relative to the gripping surface, gives the results axial displacement of the main body relative gripping assembly to move the gripping arrangement from the retracted position to compound according to the operation means included in the job.

This gripping tool thus utilizes a mechanically into gear engagement mechanism that generates its gripping force in response to actuation of the work of the axial load or axial stroke layout capture, and start operation occurring or in conjunction with the application of external axial load and an external load torsion or independently from them, in the shape of the left or right application of torque load carried across the tool from the load-bearing adapter housing configuration for gripping the grip surface layout draft load coupled with the product.

It should be clear that the usefulness of the data, or other similar tools is a function of the exciting range of products sizes, usually expressed as minimum and maximum diameters of tubulars that can be placed between the gripping surfaces in the fully retracted and fully extended position of the gripping tool, ie radial dimension and radial swing gripping surface. The usefulness of this exciting tool can be improved if the tool will be able to hold the product to the size of a wider range. The present invention addresses this need for applications where increased radial dimension and a radial course are useful, which often occurs when the adaptation of exciting tools for running tubulars oil country tubular goods.

According to a broad aspect of the present invention provides an extension control mechanisms for use in gripping the tool to provide radial travel of elongation and increasing the size of articles that can be placed in the pick-up tool having a gripping surface, which are movable gripping elements. The invention includes a control mechanism with three claw couplings with the cam pairs providing dvuhpovorotnoe axial stroke control and additional control cam mechanisms causing radial gripping surfaces move the tool as a function of the axial stroke.

Movement control with three claw couplings comprises:

lead dog clutch,

intermediate dog clutch,

driven cam clutch

leading couple cam acting between the driving cam clutch and intermediate cam clutch, and

Couple driven cam acting between the intermediate coupling wheel and the driven cam clutch.

Preferably, the leading cam couple is capable of action only causes axial move as a function of the rotation in the first rotational direction, and the driven cam pair - in the second direction of rotation, while the division dvuhpovorotnogo control two cam pairs causes the creation of a greater axial stroke and thus , radial travel gripping surface than is possible when using a single cam pair in dvuhpovorotnom control mechanism.

These and other features of the invention will become more apparent from the following description, wherein references are made to the accompanying drawings, formed only for illustration, not intended in any way to limit the scope of the invention or the specific embodiments shown. In the drawings:

FIG. 1 is an isometric view of a partially cutaway simplified version of biaxial dvuhpovorotno included in the work of the tool descent tubular products with an external capture, created in the configuration architecture with a pair of cam, shows how it should look to the right application of torque.

FIG. 2A diagram of a basic configuration with a single architecture cam pair FIG. 1 shows a two-dimensional representation of how it should look to the right application of torque.

FIG. Figure 2B architecture diagram. 2A shows a two-dimensional representation of how it should look to the right application of torque.

FIG. 3 diagram of an architecture with three claw couplings in a two-dimensional representation is shown without the application of torque.

FIG. 4A architecture diagram with three claw couplings Fig. 3 shows a two-dimensional representation of how it should look to the right application of torque.

FIG. 4B architecture diagram with three claw couplings Fig. 3 shows a two-dimensional representation of how it should look to the left of torque application.

FIG. 4C architecture diagram with three claw couplings Fig. 3 shows a two-dimensional representation of how it should look in the pick-up tool with the applied axial elongation.

FIG. 5A architecture diagram with three claw couplings with a pair of cam stops with the rise in two-dimensional representation shows how it should look to the left of torque application.

FIG. 5B architecture diagram with three claw couplings Fig. 5A with a pair of cam stops with the rise in two-dimensional representation shows how it should look like a small right turn to lift stops in the neutral position.

FIG. 5C architecture diagram with three claw couplings Fig. 5A stops with the rise in two-dimensional representation shows how it should look to the right application of torque.

FIG. 6A architecture diagram with three claw couplings Fig. 3 with a lock in two-dimensional representation shows how it should look in a fixed position.

FIG. 6B architecture diagram with three claw couplings Fig. 3 with a lock in two-dimensional representation shows how it should look right with the application of torque to the lock disconnected.

FIG. 6C architecture diagram with three claw couplings Fig. 3 with a lock in two-dimensional representation shows how it should look like a lock and disconnected from the application of the left torque.

FIG. 7A architecture diagram with three claw couplings Fig. 3 with a clamp with the possibility of locking in a two-dimensional representation shows how it should look in a fixed position.

FIG. 7B architecture diagram with three claw couplings Fig. 3 with a clamp with the possibility of locking in a two-dimensional representation shows how it should look right with the application of torque to the lock disconnected.

FIG. 7C architecture diagram with three claw couplings Fig. 3 with a clamp with the possibility of locking in a two-dimensional representation shows how it should look to lock disconnected and left torque applied.

FIG. 7D architecture diagram with three claw couplings Fig. 3 with a clamp with the possibility of locking in a two-dimensional representation shows how it should look like a disconnected clamp and compression applied on the connection to the driven cam pair.

FIG. 7E architecture diagram with three claw couplings Fig. 3 with a clamp with the possibility of locking in a two-dimensional representation shows how it should look like a disconnected clamp and compression applied on the connection to the drive cam pair.

FIG. 7F architecture diagram with three claw couplings Fig. 3 with a clamp with the possibility of locking in a two-dimensional representation shows how it should look for options with a locked latch attached and right torque.

FIG. 8 appearance of the instrument descent tubulars architecture with three claw couplings shows how it should look in a fixed position.

FIG. 9 a sectional view of the tool descent tubulars architecture with three claw couplings shows how it should look in a fixed position, with accommodation within the proximal end of the article.

FIG. 10A exterior layout with three claw couplings shows how it should look in a fixed position.

FIG. 10B a sectional view of the layout with three claw couplings shows how it should look in a fixed position.

FIG. 11A exterior layout of the retainer includes leading cam clutch retainer ring and key lock, shows how it should look in a fixed position.

FIG. 11B partially cutaway perspective view of the lock arrangement comprising driven cam clutch retainer ring and key lock, shows how it should look to the disconnected position.

FIG. 11C appearance of the layout of the retainer includes leading cam clutch retainer ring and key lock, shows how it should look to the disconnected position.

FIG. 12A exterior layout with three claw couplings shows how it should look to the right application of torque.

FIG. 12B a sectional view of the layout with three claw couplings shows how it should look to the right application of torque.

FIG. 13A exterior layout with three claw couplings shows how it should look to lock disconnected and left torque applied.

FIG. 13B a ​​sectional view of the layout with three claw couplings shows how it should look to lock disconnected and left torque applied.

Gripping instrument described in PCT patent application CA 2006/00710, consists of three main interacting components or configurations: 1) the arrangement of the body 2) exciting arrangement which carries the housing arrangement, and 3) control mechanism, acting between the housing arrangement and the exciting arrangement. The arrangement of the housing, in general, creates a constructive connection tool components and includes a load bearing coupler, whereby the load of the rotator machine or frame transfer reaction forces transmitted to the rest of the housing or arrangement of the main body or from them. An exciting arrangement has a gripping surface, the arrangement of the main body bears the housing arrangement, and the arrangement is provided with means for radial play or movement of the gripping surface from the retracted position to the coupling position in response to relative axial movement or axial stroke radial and tractive compound products with gripping surface. An exciting arrangement thus acts as including job axial load or axial stroke gripping member.

The main body is mounted coaxially with respect to the product to create an annular space, which is located to be included in the work of the axial course, exciting arrangement, coupled to the main body. The gripping arrangement adapted for exciting conformal distributed over the circumference and with the overall resistance, tractive connection to the product. The means of the radial stroke of the gripping surface, which carries the gripping arrangement operable to binding of relative axial displacement or axial travel, at least in one axial direction, radially offset or radial stroke gripping surface to the product correlating axial and overall standoff radial efforts, thus emerging, so that the radial gripping force on the gripping surface provides a reaction of the axial load and torque of the article where the distributed radial grip strength has internal resistance, the apparatus comprising actuated axial load capture mechanism, wherein the bearing axial the load is distributed between the rotator machine frame or the transmission of reactive forces and products; Freight adapter, main body and the gripping element, generally acting in series.

A control mechanism acting between the housing arrangement and the exciting arrangement is arranged to bind a relative rotation between the adapter and the load bearing surface engagement with the axial stroke exciting arrangement and thus move radially gripping surface. Included in the work axial load capture mechanism thus configured to permit relative rotation between one or both carrying the axial load of the joints, between the loading adapter and main body or main body and the pickup element, the relative rotation is limited by at least one comprises a work rotation control mechanism linking the relative rotation between the adapter and the cargo surface engagement with the gripping element move axially and thus move the radial gripping surface. Controlling mechanism or mechanisms may be implemented to create this relationship between rotation and axial stroke in numerous embodiments such as a mechanism with pivoting lever or rocker bodies acting between the arrangement enclosure and the exciting arrangement, but can also be in the form of cam pairs acting between gripping members, and at least one of the following: the main body or load bearing adapter for immediate perception, thereby and transfer axial and torsional loads causing, or seeking to cause and maintain rotation of the radial grip force. The cam pairs, acting generally, a method using a cam clutch and moving along the cam clutch cam having a contact surface formed in a preferred embodiment, the binding of their combined relative rotation, at least in one direction, with the axial stroke pickup element in capturing direction for sealing, wherein an axial stroke thus has the same effect with the axial stroke created by the axial load borne by the gripping element, and operates in association with it. Application of relative rotation between the rotator of the machine or the frame transmission of reactive forces and gripping surface in contact with the workpiece at least in one direction, thus causes radial speed or the radial displacement of the gripping surface in connection with the product with correlative axial force, torque torque and radial strength, thus arising, so that the radial gripping force on the gripping surface provides a reaction torque in a product, the apparatus comprising: including in operation torsional loads, so that with the inclusion of the work of the axial load capture mechanism automatically comes into operation in response to combined biaxial loading at least in one axial and at least one tangential or torsional direction.

Also, according to PCT patent application CA 2006/00710 arrangement with claw couplings can be used in various devices, as summarized in Table 1 herein, wherein the layout data having the "claw clutch", in Table 1, produce relative axial movement between the drive and driven cam layouts as a function of the applied relative rotation; thus the choice of local control over the relationship a step or angle of the helix, acting on the junction of a pair of cam. If this action must be dvuhpovorotnym (included in the job when the left and right rotation) and is provided with a cam arrangement consisting of one cam pair, shown and described as a sawtooth profile between the abutting profiled ends generally cylindrical and coaxially aligned rigid body, as in FIG. 11B (showing a cam sleeve used in the underlying architecture or configuration 1 of Table 1, it may appear in an external gripping tool) that are presented here again in Fig. 1, showing an arrangement of one jaw clutch having a drive coupling wheel 2 and a driven cam sleeve 3, which create a pair of cam 4, they can form with the application right rotation. Here we use the name "master" and "slave" to claw couplings for convenience in describing the relative displacements and forces. This should not be interpreted to limiting the application because, in general, the cam system described can be inverted.

FIG. 2A arrangement 1 claw couplings shown schematically in the two-dimensional representation, where the axial and tangential directions are shown as abscissa and ordinate, respectively, in the graph of FIG. 2A. The tangential position, thus representing a location on the circumference and tangential displacement is rotation. 4 shows a pair of cam abutting multistart right helical load bearing surfaces 5, the testimony here, as two passes with an intermediate angle of the helix, and the left helical load bearing surfaces 6 with two taps, shown here with a relatively small angle helix, t.e . smaller pitch than the helical load bearing surfaces 5, wherein the intersection of the helical load bearing surfaces 5 and 6 forms projections or peaks at 7. It is clear that increasing the relative rotation of the right, left helical carry ing the load surface 6 are connected, the length "C" of the tangential contacting the compound decreases, whereas the relative axial dilution "Z" (axial stroke) between the driving and driven claw couplings increases to joining position limit where additional rotation may produce a result, installation of the peaks on each other. Since the cam pair must also transfer the load actually occurs restricting position when the value of the contact is insufficient to carry the required load, providing a total displacement represented by a vector R on a graph where the axial component of R is equal to Z, ie, axial move. FIG. 2B shows this restriction to build claw couplings 1, as it should appear as a result of the application of the left leading to the rotation of the cam sleeve 2 relative to the driven cam clutch 3, causes the action right helical load-bearing surfaces 5, wherein the total displacement vector is represented by L. Thus, there limit the axial stroke and capacity (represented by the size of Z and C, respectively in FIGS. 2A and 2B) a single cam pair dvuhpovorotnogo rotation, especially when combined with other parallel activities, design parameters, such as the preferred pitch or angle helix governing how actuation of the left or right, as is clear from a comparison of the cam pair 4 in FIG. 2A and 2B at the left and right rotations, respectively. While such a configuration with a pair of cam, creating an axial stroke, as a function of the applied relative rotation in two directions, provide significant utility in some applications need to increase the speed and capacity.

One object of the present invention is to provide an agent that reduces or effectively eliminates this restriction in the operating range and capacity characteristic of the single cam pairs acting in two directions, said means for adjusting to any one of control mechanisms, known as "cam" in Table 1 PCT CA 2006/00710. FIG. 3 improved architecture claw couplings of the present invention (as in the diagram with a two-dimensional representation, where the axial and tangential directions are shown as the ordinate and the abscissa, respectively) gives the arrangement 10 with three jaw clutch having a driving dog clutch 12, the driven cam sleeve 13 and at least one intermediate sleeve 14 for camming action between the driving cam 12 and the clutch driven cam clutch 13; and hence it is called herein architecture with three claw couplings. The leading pair of cam 15 is configured to actions between the driving cam and the intermediate sleeves 12 and 14 respectively, and a pair of driven cam 16 is configured to actions between the intermediate and driven claw couplings 14 and 13 respectively. Leading cam couple 15 includes abutting stops 17 formed by relatively steep angle of the helix (shown here vertical) joint surfaces 18 stops and a relatively small angle of lifting the left helix junction surfaces 19 inclined thrusts, where mating helical surfaces 19 inclined abutments also operate in parallel from the junction of the load-bearing thread 20. The driven cam 16 consists of a pair of mating load bearing inclined sections 21 formed by abutting a relatively steep angle helix inclined surfaces 22 stops (shown here vertical) and the load-bearing right abutting helical joined surfaces 23 inclined thrusts, is shown having an intermediate helix angle (similar to the load-bearing right helical surfaces 5 shown for the cam pair 4 in FIG. 1).

FIG. 4A shows an arrangement 10 with three claw couplings, how it should look to the application of a right rotation, causes the relative displacement of the leading cam pairs 15, initially causes a dilution of the surfaces 18 stops and a sufficient rotation also causes dilution of surfaces 19 angled abutments so that the load is completely bear mating threads 20 on the load carrying or displacement in the range specified by the vector R. Now it should be clear that the right rotation speed and axial load bearing capacity of a pair of cam 15 is not limited to the useful length of the contact surface 19 of the spiral inclined thrusts, but only limited load-bearing threads 20, which can be easily made to create a connection of sufficient length and strength to ensure adequate strength with virtually unlimited axial stroke, effectively eliminating the restrictions for design purposes. In fact, the inclined surface 19 of the stops are redundant and do not need to connect.

As also shown in FIG. 4A, the corners of the helix bearing the inclined portions 21 and surfaces 22 sloping abutments forming a driven cam pair 16 is selected based on the angle of the helix load bearing thread 20, and other variables such as friction, as will be clear to those skilled in the art art, so that under the action extends or retracts right rotation, no displacement occurs in the driven cam 16 pair.

FIG. 4B shows an arrangement 10 with cam clutches, it should look like with the application of left rotation driving cam sleeve 12 relative to the driven jaw clutch 13. In this case, the driven cam 16, the pair is active and operates in a manner similar to that described above for the pair of driving cam 15, with inverse directions of helix angle of the load bearing inclined portions. Attachment of the left rotation to the driving cam sleeve 12 causes the breeding surfaces 21 sloping abutments and korellyativny sliding contact on the load-bearing of the helical surfaces 23 causes displacement of the intermediate jaw clutch 14 and the driving cam sleeve 12 axially upwardly relative to the driven cam sleeve 13, creating a bias in the range indicated vector L. In the axial load and the load torque from the left, which carries the arrangement 10 with three claw couplings reacts leading cam pair 15, which stops 17 by selecting the helix angle at the contact surfaces 18 and stops the installation can be performed for control method response to a load through a pair of drive cam 15 for voltage regulation and prevention zakontrivaniya torsional loads on the threads of the intermediate cam sleeve 14 with the driving cam sleeve 12 due to their connection to the load-bearing thread 20, ie friction locking threaded on the type of nut and bolt. Also, similar to the behavior at the right rotation, described above, helix angle load bearing inclined portions 21 is selected corresponding corner helix load bearing thread 20, so that under the action of the left rotating to advance or retract no displacement occurs in the leading cam pair 15.

Now it should be clear that the arrangement 10 with three claw couplings designed cam pair (a pair of driving cam 15 and the driven cam 16 a pair): one active and creates an axial stroke when right rotation when the second is static; and the second active and creates an axial stroke during rotation of the left, when the first is static.

Comparison of vectors R and L are offset in FIG. 2A and 2B with the vectors in FIG. 4A and 4B, respectively, show that for comparable geometrical parameters axial stroke greater magnitude can be obtained as in the right and left rotation with the drive and driven cam pairs 15 and 16 (FIG. 4A and B) in the architecture 10 with three cam clutches, than can be obtained with a single operating in two directions, a pair of cam 4 (FIG. 2A and B).

As also shown in FIG. 4B, the above described ideas for incorporating a load-bearing thread 20 of the driving cam 15 pairs it should be clear that it is possible to create a load bearing thread 20, for use in conjunction with a helical abutting load bearing surfaces 23 to increase the speed and load capacity; however, in some applications, the tools lowering tubulars may be preferable to provide free breeding driving and driven clutch wheels 12 and 13, respectively, which provides the configuration shown in FIG. 4C, where the intermediate dog clutch 14 remains connected load-bearing threads 20 with the driving dog clutch 12, but not connected, so the driven cam sleeve 13, providing free cultivation which may be required for actuating engagement with the application of the axial load without simultaneously active rotation when the arrangement 10 with three claw couplings used for example in the base (Configuration 1) architecture gripping tool shown in Fig. 1.

As an interim architecture (not shown), wherein the load bearing thread 20 connecting the driven coupling wheel 13 and intermediate cam sleeve 14 are required, and still requires some degree analogous freedom for axial dilution load bearing thread 20 may be provided with significant lateral clearance . It should be apparent to those skilled in the art that for a single-pass active thread backlash is limited only to the magnitude of a thread pitch less than the required thickness of the crests of the thread, so that a large free axial dilution can be obtained for applications where it is possible to use a relatively larger pitch t.e . applications where a low helix angle is required.

As an additional intermediate architectures (not shown), the two pairs of cam may be formed as a surface inclined thrusts continuing load bearing thread 20 (with a small lateral gap) that can be called architecture with four claw couplings (not shown). Architecture four claw couplings can be performed with the fourth kulachovym component having a restriction, providing axial movement, but prevent rotation relative to the driven cam sleeve, and rigidly fixed to the arrangement of capture, so that upon release of the retainer arrangement with cam clutches supports free axial stroke for connection with the product under the influence of the deflection load. Such a device can be useful if you want to move ahead in the architecture can be taken with three claw couplings (particularly limited device driven cam pairs).

Also in FIG. 4B shows the sum of the axial height and therefore the bearing capacity of the stops 17, which is a function of pitch or the angle of the helix, is selected for the junction of the load-bearing thread 20 (and similarly surface 19 inclined stops), so that for applications where low angle helix thread is preferred, it becomes difficult to provide sufficient strength to react the torsional loads on the left, which is achieved by the stops 17 correlatively with low axial height. For such applications an additional object of the present invention is to provide means for overcoming this limitation by replacing the intermediate dog clutch 14 in the arrangement 10 with three cam clutches, as shown in FIG. 5A, the arrangement 30 with intermediate claw couplings, acting between the driving cam clutch 12 and the driven cam 13. The clutch assembly 30 with intermediate claw couplings consists of the auxiliary ring 31 stops and lift the pipe 32 with the intermediate cam clutch, where a pair of cam 33 with the rise stops made with the possibility of action between the ring with 31 stops and the pipe 32 with the intermediate cam clutch. Cam pair of stops 33 with the rise surface 34 is inclined with raised portions and the surface 35 with their catchers. The general arrangement of the cam 30 with the intermediate sleeve acts in a manner analogous to the intermediate cam sleeve 14 in case of applying a clockwise and counterclockwise rotation, as shown in FIG. 4A and 4B and described above for the arrangement 10 with three claw couplings. If one compares FIG. 4B and 5A action of the ring 31 lifting stops when the application of left torque, it is obvious where the left torque causes the movement of the ring 31 with stops up against surfaces 34 raised inclined portions, creating a complete connection surfaces 18 stops, so that the combined height of the surface 18 thrusts thus becomes greater, when used with a ring architecture lift stops. It should also be understood that the helix angle surfaces raised inclined portions are selected consistent with the angle of the helix surfaces 18 stops to generate said complete connection surfaces 18 stops at the left rotation, and similarly, link lengths of surfaces 34 raised inclined portions correlatively performed for to provide sufficient strength to carry the loads to which the surface 18 stops responding. FIG. 5B shows an arrangement 30 with three claw couplings with moderate right rotation, the ring 31 lifting stops shown completely slipped down the surface 34 raised inclined portions (cam of steam 33 in the fully retracted position), the movement can be varied to create the following: prior contact with the surface 19 inclined abutment right rotation (where the helix angle of inclined surface 19 of the stops is selected in concert with the angle of the helix raised catching surfaces 34 for creating such movement); gravity; or deviation of springs (not shown) applies a force to the pipe retractor 32 with intermediate claw couplings. With regard to this provision cam of steam 15 is designed so that the surface 18 stops have some degree of overlap, large enough for 'zalavlivaniya' when applied clockwise rotation, but 'pass without contact' in the case of applying an additional clockwise rotation, causes an additional axial stroke limited load bearing thread 20, as shown in FIG. 5C.

As shown in FIG. 4C, in some embodiments, the application must be limited free axial dilution, is provided between the drive and driven claw couplings 12 and 13, respectively, creating a lock specifically, to support removal and insertion of purely mechanical gripping tool, as described in PCT CA 2006/00710. Therefore, a further object of the present invention is to provide a lock which functions in the architecture with three claw couplings supporting the leading cam lock clutch 12 to the driven cam sleeve 13 as shown in FIG. 6A, where the retainer 40 is shown with the arrangement 10 with three claw couplings, again in the two-dimensional representation, where the radial plane in which the signs carried retainer 40 is generally different from the above features of the arrangement 10 with three claw couplings. The ring 41 retainer is generally tubular body tightly fixed and coaxially mounted on the driven cam clutch 13 eligible helical grooves 42, which are placed firmly fixing tabs 43 lock, with key 43 clamp rigidly attached to the driven cam clutch with According to the device that holds the retainer ring 41 to move axially only between extended and retracted positions with respect to the driven cam clutch 13, defining the course of the retainer on the helical path with a predetermined length of helical grooves 42 with respect to the length of the lock key 43. Cam pair 47 arranged to clamp action between the ring 41 and the leading cam lock clutch 12, and is formed, in general, abutting profiled latch hooks 44 having a selected height slightly less than the selected course retainer and having a rear surface 45. The hooks 44 latch shown compounds in position in FIG. 6A and in a position to prevent axial dilution leading cam sleeve 12 and the driven cam sleeve 13, while on the axial load, the effect of which may otherwise breed them reacts driving dog clutch 12 through the hooks 44 lock ring 41 lock and dowels 43 Lock held in helical grooves 42 and splines 43 on the driven latch dog clutch 13 to which the fastener tabs 43 are fastened. However, with the right rotation, as shown in FIG. 6B, the hooks 44 tend to disengage the lock and the lock ring 41 is free to draw, secured by keys 43 in the right-hand helical grooves 42, which can be created by drawing different tracks: the force of gravity; deflection of the spring 46 acting between the retainer ring 41 and the driven cam clutch 13; or a sufficient rotation, the contact surfaces 45 of rear hooks helix angles, abutting the rear surface 45 of the hook, respectively, selected from the helix angle grooves 42 to create a force retractors. With the application of left rotation and the cam pair 16, docked, as shown in FIG. 6B, ie without dilution axial sufficient grip hooks fastener 44 also configured to re-lock the hooks 44. However, if the leading first dog clutch 12 rises, causing axial dilution compound sufficient to prevent latch hooks 44, then counter-clockwise rotation is applied, as shown in FIG. 6C, re-fixing is prevented, and a pair of cam 16 is active, causing an axial stroke.

The process of operating the system shown in FIG. 6A-6C and the above-described arrangement with the beginning of the claw couplings in a fixed position can be described in two phases as follows:

1. Installation of the instrument (in the product).

2. Turn right (to release the lock and connections leading cam pairs).

In the case of using the tool for connection with the bracing units driven cam pairs are required the following two additional steps:

3a. Pick up an instrument.

3b. Turn left (for connecting the driven cam pairs).

The workflow tool by disconnecting the product is similar to the simple and also requires two or three steps from the inclined sections breakout or bond, respectively, were as follows:

1. Installation tools.

2. Turn left (to draw the layout of capture and lock connection).

Where to fix the tool driven by the cam pair requires one the following additional steps:

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

Provided ease of operation is not projected or not a random event may lead to the simultaneous application of sufficient left torque, rotation and compression to a tool for connecting the lock and if these events are relatively frequent, risk of unintended fixation and therefore detaching layout capture of the product may be unacceptable. In such applications, where it is necessary to limit the axial free breeding, provided between the drive and driven clutches creation latch specifically to support inserting and removing entirely mechanical gripping tool may also be required to prevent accidental locking compound. In this regard, a further object of the present invention is to provide a locking mechanism operatively associated with the architecture with three clutches and cam lock shown in Fig. 4 and 6A-6C, respectively. A further preferred embodiment of the present invention is shown in a two-dimensional diagram of FIG. 7A-7F and described herein. This embodiment is an integrated mechanical locking device operable to enable the locking arrangement in place with cam clutches FIG. 6A-6C. The process of working device equipped with a locking arrangement claw couplings can be described in the following six steps:

1. Installation of the instrument (in the product).

2. Turn right (to release the lock).

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

4. Turn left (for connecting the driven cam pairs).

5. Installation of the instrument (for spring).

6. Turning to the right (to connect the locking mechanism, the compounds leading cam pairs and gripping the product).

Where required an additional step to the next breakout units:

7. Turning to the left (for connecting the driven cam and a pair of gripping articles).

The process of working to release the locking mechanism and fixing the position of the bonding tool also requires the following six steps:

1. Installation (for connecting a leading cam pairs).

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

3. Pick up (for bounce lock).

4. Turn right (to move back a leading cam pairs).

5. Installation (plant for compound leading cam pairs).

6. Turn left (to draw capture and layout tools with a lock).

If you start from the junction driven cam pairs takes one the following additional steps:

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

From the above procedure, it is clear that additional stages reduce the risk of accidental detachment, by increasing the complexity of operation.

FIG. 7A shows the architecture of a three-claw couplings with built-in mechanical lock on the circuit with a two-dimensional representation of how it should look to the United striker. The arrangement with the three claw couplings with a locking cam has a leading sleeve 12, a driven dog clutch 13, intermediate clutch 14 and a cam 40. The cam lock clamp pair 47 is configured to action between the frame 41 and the leading cam lock clutch 12, and is formed, in general, the hooks 44 Profile clamp joints. Profile 45 of the hook fastener on the housing 41 of the retainer includes a stop 61 blocking the upper side 62 and the profile 45 of the hook fastener driving cam sleeve 12 has a generally joints socket 63 under the thrust block at the bottom side 64 and the space for the stop interlock on 69. The angles of the upper side faces 65 and 66 of locking stops is selected in conjunction with the angles of faces 67 and 68 slots under the palm and the geometry of the lock keyway 42 for coupling the lock detachably locks and releases the lock housing during bonding. Keyways 42 of the housing 41 and the lock key 43 is rigidly attached to the driven cam clutch 13, are a pair of locking faces 70 consisting generally of the mating faces 71 and 72 locks. The angle of the faces 71 and 72 are selected together with the locking angle of the load-bearing thread 20 to prevent accidental release of the lock due to vibration and reduce uncertainty compounds the stop position 61 on the bottom of the lock profile 45 of the hook fastener driving dog clutch 12. The driven coupling wheel 13 has a compression spring 73 with the restriction stroke, prestressed, when the latch 40 is disconnected, the yoke spring 46 pushes the face of the housing 41 lock 74 in contact with the stop 75 of the spring. Stiffness coefficient and the compressive prestress of the spring 73 is selected in conjunction with the stiffness coefficient and prestressed biasing spring 46 so that spring 73 does not shrink after its initial position under prestress load biasing spring 46 and any non-standard loads include weight component.

FIG. 7B shows an arrangement with cam clutches FIG. 7A on the scheme with a two-dimensional representation of how it should look to the disconnected retainer and faces the hook clamps in contact, compressing the spring 73 is fully extended, and contact with the housing 41 lock sets it so that the edge of the hook profile 45 of the hook fastener are overlapping and sliding connection . The keys 43 are installed in the helical section 77 of the keyway 42 such that clockwise rotation must condition the detaching profile of a hook fastener and left rotation must condition the helical sliding housing 41 latches on the keyway slots 42 and the connection of the hook profile 45 of the hook latch extension biasing spring 46 for setting the layout in position shown in FIG. 7A.

FIG. 7C shows an arrangement with cam clutches FIG. 7A on the scheme with a two-dimensional representation of how it should look like a disconnected clamp and with the application of the left torque, with the combined helical ramps 23, load carrying driven cam pairs 16 and connected helical surfaces 19 inclined stops and abutting surfaces 18 stops driving the cam pair 15.

FIG. 7D shows an arrangement with claw couplings Fig. 7A on the scheme with a two-dimensional representation of how it should look under compressive load after connecting a pair of driven cam 16. All joints brink as the leading pair of the cam 15 and the driven cam pair 16 are connected and layout with claw couplings 10 is under compression. The face 74 of the body 41 is connected with the focus lock spring 75 and the compression spring 73 is compressed the position of prestressing. The keys 43 are set in the helical section 77 of the keyway 42. The lock block 61 is connected to the socket 63 under the palm lock. The application of the right rotation to the driving cam clutch should move the latch body 41 in the locked position, leading the verge of 71 and 72 pairs of 70 locks into the mix.

FIG. 7E shows an arrangement with claw couplings Fig. 7A on the scheme with a two-dimensional representation of how it should look to release the lock 40 and the leading cam clutch 12 and the housing 41 lock set for detaching the application lock left rotation with respect to the driven cam profile coupling 13. The sole clamp 45 leading dog clutch 12 slidably connected to face 65 block 61 block, and left rotation step leading claw coupling should give a result similar to the movement of the housing 41 lock with respect to the driven cam clutch 13 and the intermediate cam clutch 14, the next working axial movement of the leading dog clutch 12 should be subject to the movement of the key 43 Section 76 of the lock in the helical section 77 of the keyway 42.

FIG. 7F shows an arrangement with claw couplings Fig. 7A on a two-dimensional representation of the pattern as it should appear unlocked and with the application leading to the right-hand rotation of the cam sleeve 12 relative to the driven cam sleeve 13 and the intermediate dog clutch 14. It is understood that, as shown in the unlocked position as the leading pair of cam 15 so and a pair of driven cam 16 may be applicable.

It should now be appreciated that the architecture with integrated mechanical lock of the present invention is well adapted to stop random fixation architecture with three claw couplings of the present invention, due to reduced likelihood of additional steps in the sequence required fixation occurring randomly.

It is understood that the retainer can lock close means which include, but are not limited to, mechanical and hydraulic means.

Similarly, other devices can be created between the leading cam lock clutch 12 and the driven dog clutch 13. One such configuration (not shown) deflects the retainer ring 41 in a normally extended position. With the right rotation lock ring 41 tends to push the latch hooks 44 from the position connections. Latch hooks are shaped distribution and to prevent partial connections in intermediate positions during the rotation (one rotation or less), which should otherwise occur partial connection preventing clockwise rotation, that provides a step load bearing thread 20 and the height of the selected latch hooks 44.

It should now be appreciated that the architecture with three claw couplings with latching of the present invention is well suited to the creation of additional radial stroke, which may be advantageous with external gripping tool, such as shown in FIG. 1, where, for example, this is normally necessary to grip connected tubulars in the size range below the coupling.

Architecture with three gripping claw couplings inside (with internal gripping) tool descent tubulars

FIG. 8-13B shows, described below, the preferred embodiment of the improved gripping tool, referred to herein as a "tool descent tubular products with internal capture of architecture with three claw couplings." FIG. 8 shows the appearance of the instrument descent tubulars of a preferred embodiment, generally indicated at 100, and shows how it should look in the configuration of a latch having a housing arrangement 110 and layout 120 pickup element.

FIG. 9 is a sectional view tools 100 shutter tubulars it should look like in configuration and installed inside a lock on the same radius from the proximal end 101 of the product 102. The tool 100 is configured lowering tubulars at the upper end 105 for connection with the hollow shaft of the top drive, or lower end of the column drive components, to which is attached (not shown) carrying a load adapter 112 is built into the spindle 130 such that spindle 130 acts as a main tool body 100 tour. The load bearing coupler 112 is generally axisymmetric and made from a material suitable strength. It has an upper end 121 configured with internal threads 122 suitable for sealing engagement with the hollow shaft of the top drive with an internal through bore 123, the spindle 130 continuing channel.

Also shown in FIG. 9 tool 100 has a shutter arrangement tubulars body 110 consisting of an elongate, generally cylindrical spindle 130 having an upper end 131, lower end 132 with external surface 133 of a frustoconical, and an inner channel 136. The spindle 130 is threaded at 134 and splined housing member 135 at the upper end 131. The tool 100 is provided with a shutter tubulars locking ring 140 having a splined section 142 at the lower end 141. A locking ring 140 is shown having a generally tubular outer sleeve 184 located outside the load-bearing adapter 112 and tightly fixed to it, where the outer sleeve 184 is designed to protect the load-bearing adapter 112 from damage tong. The spindle 130 carries an inner axially into operation capture arrangement 120 having an elongated and generally cylindrical lower end 109 that is inserted into the upper proximal end 101 and tubular 102 coaxially placeable therein. Layout 120 capture consists of a casing 144 with an upper end 145 and lower end 146 having a threaded member 147 at the lower end 146, an axial retaining groove 148 and a plurality of radially oriented windows 149, arranged circumferentially on the lower end 146 in which are located the jaws 160 . In general, the elongated jaws 160, the upper end 161, lower end 162, inner surface 163, an external gripping surface 164 and parallel sides (not shown) have a plurality of contact faces 166 in the form of a truncated cone inner surface 163 connecting seam with two surfaces 133 frustoconical spindle 130 forming a junction 114 slips acting to create the radial travel of the jaws 160 in response to axial actuation.

As also shown in FIG. 9, the tool 100 lowering tubulars has dvuhpovorotny mechanism 200 control the actuation of the axial stroke with three claw couplings with latching generally configured with architecture with three claw couplings, and includes a driving dog clutch 220, the driven cam sleeve 260 and the intermediate dog clutch 240. The control mechanism 200 operates between the spindle 130 and the arrangement 120 and capture arrangement 180 includes a housing including a slave and master cam covers 181 and 182, respectively. Control mechanism 200 with three claw couplings with locking function and is arranged, generally as described above and shown in the diagram of FIG. 3-4C and 6A-6C.

FIG. 10A shows the control mechanism 200 is configured with a latch, the arrangement of which is provided with a driving dog clutch 220 with the upper end 222. As shown in FIG. 10B on a section layout 200 with three claw couplings in a configuration with a lock, the arrangement 200 with three claw couplings has a leading dog clutch 220 with the lower end 223, outer surface 224 and inner surface 225, and one or more projections 226 transmit torque (hereinafter eight shown) at the upper end 222. The inner surface 225 leading cam sleeve 220 has a threaded member 227 at the upper end 222 and a seal member 228 at the lower end 223. As also shown in FIG. 9, the threads 134 on the spindle housing 130 are screwed to threaded member 227 on the master cam sleeve 220 and the sealing member 228 sealingly connected to the outer surface of the spindle 130. The slotted section 142 of the locking ring 140 engages with the projections as the torque transmission (not visible in this form section, but are shown in FIG. 10B numeral 226) on the drive cam sleeve 220 and slotted element 135 on the spindle 130 so that the driving dog clutch 220 are structurally and rigidly fixed to the spindle 130 and prevented from its movement, both axially and circumferentially relative to the spindle 130. As also shown in FIG. 10B, the bottom side 229 driving the cam sleeve 220 includes hooks 230 latch repeated. The outer surface 224 leading cam sleeve 220 includes a plurality of load-bearing threads 231 at the lower end 223. The load-bearing threads 231 generally consist of a buttress thread with a load bearing side face 233 of the thread profile and the guide lateral side 234 of the thread profile. Leading cam sleeve 220 has a seal member 236 on the outer surface 224 at the upper end 222. As also shown in FIG. 10A, the leading camming surface 220 has a sleeve 232 stops and the inclined surface 237 stops, placed on the downwardly facing outer surface 224 of the ledge 296 at the top end 222.

As also shown in FIG. 10A, the intermediate dog clutch 240 with the upper end 241, lower end 242, an inner surface (not shown) and the outer surface 244 has one or more surfaces 245 stops (shown here three) onto the upper end 241 of connecting the surfaces 232 stops at the upper end 222 leading cam sleeve 220, together forming a pair of surfaces 255 stops. Also at the upper end 241 of the intermediate cam sleeve 240 are one or more (three shown) stops the inclined surfaces 256 which are joined with a sliding connection sloping surfaces 237 stops driving dog clutch 220, together forming a pair of inclined surfaces 257 stops. As also shown in FIG. 10B, the intermediate dog clutch 240 has a load bearing thread 246 (shown here as a form of a multiple thread with a thread pitch, which coincides with the step helix surfaces 256 inclined stops) on the inner surface 243 at the upper end 241, and the data of thread are formed as pushing thread with load bearing side face 247 of the thread profile and the guide lateral side 248 of the thread profile and joined sliding connection with the load-bearing thread 231 leading cam sleeve 220, forming a load bearing thread pair 268 and thus, by combining with a pair of 255 abutment surfaces and a pair of 257 surfaces inclined abutments together forming the leading pair 249 of the cam sleeve 249. In FIG. 10A intermediate dog clutch 240 has one or more (here shown six) helical load bearing surfaces 250 inclined portions located adjacent to an equal number of load bearing surfaces 251 of the stops and being on the same radius with them, the lower end 242.

As also shown in FIG. 10A, the driven dog clutch 260 with the upper end 261, lower end 262 and outer surface 263 has a plurality of helical load bearing surfaces of the inclined portions 265 placed adjacent to the surface 266 stops, the load bearing and located on the same radius with them at the upper end 261. The helical surface 265 inclined portions, load bearing, and the surface 266 stops, the load-bearing, the driven cam sleeve 260 are joined sliding connection with the helical surfaces 250 inclined portions, load bearing, and the surfaces 251 stops, the load-bearing intermediate dog clutch 240, together forming a driven cam pair 267. As shown in FIG. 10B, the driven cam sleeve 260 has one or more projections 269 transmit torque, in this case, twelve (12) on the bottom side 270 to the lower end 262. As shown in FIG. 9, projections 269 transmit torque driven cam sleeve 260 are joined with projections 143 transmit torque to the upper end 145 a casing 144 and in this embodiment, are connected together using bolts in holes 297 for bolts (bolts not shown) to the structure and the rigid connection of the driven jaw clutch 260 with the housing 144. As also shown in FIG. 10B, the inner surface 264 at the lower end of the cam 262 driven coupling 260 has a sealing member 273 and an upwardly facing shoulder 274 and the outer surface 263 at the lower end 262 has a seal member 275.

As also shown in FIG. 10B, the cam clutch assembly 200 is generally tubular in shape, the retainer ring 300 with top end 301, bottom end 302 and an inner surface 303. In FIG. 11 shows the arrangement of the lead cam clutch 220, retainer ring 300 and tabs 290 latch lock ring 300 has a plurality of helical slots 305 latch tongues (here shown six), which may be evenly spaced around the circumference of the outer surface 304. Slots 305 have internal splines retainer faces 306, bearing faces 307 and helical faces 309 and 310 of sliding cams. The inner face of the socket 306, 305 has a key lock groove 308 space the pin extending to the inner surface 303 of the ring retainer 300. As also shown in FIG. 10B, the lower end 302 of the ring retainer 300 on the inner surface 303 has an upwardly facing shoulder 315. The upper side 312 at the upper end 301 of cam ring 300 has repeating latch hooks 313 latch. The hooks 313 latch on the cam ring 300 clamp joined with hooks 230 latch onto the bottom side 229 driving the cam clutch 220, together forming a pair of 314 hooks latch hooks 230 and 313 latch is selected so that when connecting the pair 314 hooks latch prevents relative axial movement of the driven cam coupling 260 and driving cam sleeve 220.

As also shown in FIG. 11A, the retainer ring 300 is arranged so that the tabs 290 are placed inside the lock socket 305 retainer dowels. FIG. 11B shows a partially sectional view of part of the layout with jaw clutch comprising a driven cam ring 260, the ring 300 Lock pin 337 Lock tabs 290 latch and spring elements 346 and 349, pins 337 locking eyelets 338 retainer (not shown on this view) is rigidly secured to the driven cam sleeve 260 and pass through a dog clutch for a sliding connection holes 291 by shear pins 290 in the keyed lock. As shown in Figure 10A, the radially targeting well pin 337 latch in association with radially orient the eye 338 retainer, which is not aligned in a radial plane with the pin 337 latch together restrict movement of tabs 290 latch relative to driven cam sleeve 260 so that the movement of the ring 300 clamp restricted helical relatively moving the dog clutch 260 driven by the value formed by the relative difference between the axial length, as shown in FIG. 11A, 290 keyed lock and key lock socket 305. Also, as shown in FIG. 11B, the lock pin 337 to the inner ends 339 are put forward through the slot 308 in the socket space retainer keys 305, and slidably connected to the openings 323 by the pins in the retaining ring 320 and retaining ring together define the movement of the retaining ring 320 relative to the driven cam ring 260. Also, as shown in FIG. 11A, assembled load bearing faces 293 key 290 clamp and the load bearing faces 307 of the ring 300 latch together form a pair 315 of load bearing faces, when the locking axial load is transmitted from the driven cam sleeve 220 (not seen in this view) on the ring 300 clamp through 315 pair of load bearing faces. Helically moving kulachovye faces 296 and 297 of tongues 290 latch and helical cam faces 309 and 310 of rings 300 clamp together to form pairs 317 and 318 of the helical sliding cam faces, respectively, so that when the tabs 290 latch are moved up or down relative to the ring 300 latch pairs 317 or 318, respectively, are connected to the cam faces. FIG. 11C shows a part of the layout, including the lead dog clutch 220, the ring 300 lock and key 290 retainer, it should look at the initial right rotation of the drive cam clutch 220, the ring 300 retainer is pushed down to the position shown in which the hooks 314 still have a small overlap 316 for re-locking under the influence of the left rotation, as shown in FIG. 6B and described above, but do not interfere under the subsequent condition the axial rotation of the right course, limited movement along the load-bearing threads 231. Also, as shown in FIG. 10B, the arrangement 200 with three claw couplings may have a spring member 346, in this case, a coil spring disposed inside the ring 300 clamp and working in compression between the retaining spring ring 320 and ring 300 latch so that the spring member 346 normally operates in conjunction with the force gravity and operates by rejecting the retainer ring 300 in an axial bottom position.

Also, as shown in FIG. 9, assembly 200 with three claw couplings positioned within the layout 180 of the cam housing consisting of a housing 181 driven jaw clutch fixedly attached to the driven cam sleeve 260 and sealingly connected to the sealing member 275 and the housing 182 leading cam sleeve rigidly attached to the drive cam sleeve 220 and sealingly connected to the sealing member 236, while the layout 180 housing creating a sealed chamber 183 dog clutch adding pressurized gas in the chamber 183, functioning as a spring, tending to bias the arrangement 122 of capture in connection with the article 102, after disconnecting the retainer 295.

FIG. 10A on the external layout view 200 with three claw couplings shown should look like arrangement in a fixed position where the leading dog clutch 220, the driven coupling wheel 260 having a minimum axial spacing, so that the driving cam pair (not shown), a pair 255 abutment surfaces, and a pair of inclined surfaces 257 and stops driving the intermediate jaw clutches 220 and 240, respectively, are connected, and the driven cam pair 267 and the intermediate trailing claw couplings 240 and 260 are respectively connected. FIG. 10B is a sectional view arrangement 10 with three claw couplings in a configuration with a lock provided with the lock ring 300, latch 295 which is disposed within the same radius and with the arrangement 200 with three claw couplings and is described above and shown in FIG. 6A-6C. Latch 295 provides a means to prevent the free axial dilution driving and driven clutch wheels 220 and 260, respectively.

FIG. 12A shows the appearance of the layout 200 with three claw couplings, how it should look to the right application of torque, driving a pair of cam 249 is engaged and the dog clutch 220 leads passed two-thirds of turnover with respect to the driven cam clutch 260 and the intermediate dog clutch 240. The load-bearing steam 268 abutment surface and the driven cam pair 267 are engaged, reacting both the axial and in the torsional load between the driven cam and the intermediate sleeve 260 and 240, respectively. FIG. 12B is a sectional view layout 200 with three claw couplings, how it should look right with the application of torque as described above and shown in FIG. 12A. The retainer ring 295 is disconnected and the latch 300 is in the lower position, biased by gravity (in this orientation) and a spring member 346 so that the lower portion 302 of the ring retainer 300 is connected to the spring member 349. The spring member 349 is a relatively stiff spring in this embodiment a stack of Belleville springs, consisting of three Belleville washers arranged in parallel and pre-compressed so that the combined force of the deflecting element acting on the ring 300 Lock negligible relative preloading the spring member 349 and, therefore, the position of the spring element 349 is known and, therefore, the axial position of the downward displacement of the retainer ring 300 is also known. The spring member 349 operates to prevent excessive loading of the retainer hooks 314 when a compressive load is applied to the arrangement 200 with three claw couplings with only a limited pair of hooks 314 latch connection. The left helical leading cam pair 255 in this case in the form of American resistant trapezoidal thread with six taps, provides rotation for causing axial stroke exceeding one full rotation which is greater than is possible with a single cam pair of counter-rotatable, as described above and shown in Figures . 2A and 2B.

FIG. 13A shows the appearance of the layout 200 with three claw couplings, how it should look to the disconnected retainer 295 and under the application of the left torque driven cam of steam 267 is connected, and the leading and intermediate cam clutches 220 and 240, respectively, were relatively small rotation relative driven cam sleeve 260. A pair of abutment surfaces 255 and a pair of helical surfaces inclined abutments 257 are connected to respond to the axial and torsional loads between the driving cam clutch 220 and the intermediate cam sleeve 240. In FIG. 13B is a sectional view layout 200 with three claw couplings as it should appear on the detached retainer 295 and in the case of application of left torque lock ring 300 downward deflated so that the lower portion 302 of the ring retainer 300 is in contact with the spring member 349. For moving arrangement 200 with three fixed claw couplings of the configuration described above and shown in FIG. 9A and 9B, in the configuration shown in FIG. 13A and 12B, must first attach right torque for disconnect latch 295, and then apply an axial displacement sufficient to move the hooks 314 latch beyond the overlap (see. FIG. 11B), so that under the influence of the applied left torque driven cam pair 267 should communicate without interference from the latch hooks 314. As also shown in FIG. 9, the axial stroke required to move the latch hooks 314 outside the compound is capable of getting into the play the instrument, ie axial stroke required before a possible connection gripping arrangement 120 with the product 102. The right pair of helical driven cam 267, in this case shestizahodny sloping section, creating an axial and torsional load progress with the application of the left angle of rotation on the intermediate coupling wheel and also provides a free axial intermediate dilution and driven claw couplings 240 and 260, respectively, if the retainer 295 is disconnected, allowing the action of the axial stroke gripping tool 100 for gripping the 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 to mean that items following the word are included in the composition, but the positions are not specifically mentioned are not excluded. Reference to an element with the indefinite article "a" does not exclude the presence of several elements, unless the context clearly requires the presence of one and only one element.

One skilled in the art will appreciate that it is possible to make modifications of the illustrated embodiments without departing from the spirit and scope of the invention as defined hereinafter in the claims.