CA2118608C - Portable top drive assembly - Google Patents
Portable top drive assemblyInfo
- Publication number
- CA2118608C CA2118608C CA002118608A CA2118608A CA2118608C CA 2118608 C CA2118608 C CA 2118608C CA 002118608 A CA002118608 A CA 002118608A CA 2118608 A CA2118608 A CA 2118608A CA 2118608 C CA2118608 C CA 2118608C
- Authority
- CA
- Canada
- Prior art keywords
- track
- derrick
- housing
- top drive
- torque
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
Classifications
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- E—FIXED CONSTRUCTIONS
- E21—EARTH DRILLING; MINING
- E21B—EARTH DRILLING, e.g. DEEP DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B19/00—Handling rods, casings, tubes or the like outside the borehole, e.g. in the derrick; Apparatus for feeding the rods or cables
- E21B19/16—Connecting or disconnecting pipe couplings or joints
Abstract
The assembly is designed to convert a conventional land rig to "top drive". It comprises a torque track that is shipped in sections and is assembled to form a rigid track extending vertically in the derrick. The track is rigidly attached to the derrick only at its base, so that the track is free to twist and-deflect laterally along its length. The housing of the top drive is connected by an angled, pivotally mounted link means with a tubular bushing that embraces and slides along the track. The link means and bushing are adapted to restrain rotation of the housing relative to the track, while transmitting both side and torque reactive loads to the track. The angled pivoting link enables the top drive to be displaced outwardly to a position over the mousehole. The top drive incorporates a hydraulic motor and gear drive assembly for rotating a drive shaft connecting the drill string and hoisting means. The housing does not carry the drill string load and can be made lighter and more compact as a result.
Description
FIEL.D OF T~E INVENTION 2 1 18 ~ 0 8 2 This invention relates to a top drive assembly for use 3 in rotating the drill string of an oilfield drilling rig.
4 R~ O~ND OF TEIlS lNVL.. ~ ION
It has previously been common in well drilling to 6 impart rotational drilling or hoisting forces to a drill string 7 using a top drive unit mounted to a guide track extending 8 upwardly within a rig derrick. These top drive units use either 9 electric or hydraulic power. The units are generally large and are designed primarily for offshore rigs, although they have been 11 installed in land rigs.
12 In prior applications, the rig derrick has had to be 13 modified to some degree, usually through welding, to be able to 14 accept the size of the machine, the track on which the top drive unit travels, and to be able to accept the torque imparted to the 16 derrick from the top drive unit through the track. In some 17 installations, the derrick has had to be extended to accommodate 18 the top drive unit. In most cases, the rig's travelling blocks 19 and/or rotary drilling swivel have had to be replaced or modified in order to work with the top drive unit.
21 Top drive implementation requires a reactive torque 22 absorbing means. This is provided by a vertical guide track or 23 a tensioned cabIe secured to the derrick. The tensioned cable 24 puts high vertical loads on the derrick, forcing a deration of the hook load capacity. Guide tracks have generally been secured 2~1860~
1 to the derrick in a manner such that significant reactive torque 2 is transmitted to the derrick structure along its length, which 3 has generally been designed for heavy vertical and only nominal 4 torque loads; this has required structural modifications to compensate.
6One type of reactive torque absorbing means that has 7 been used specifically to reduce reactive torque loads on the 8derrick is disclosed in United States patent No. 2,998,084, 9 issued to Johnson et al. This patent teaches a top drive and track having an interconnecting pivoting linkage apparatus. The 11 linkage pivots about vertical axes; it is unable to transfer side 12 loading and transmits pure rotational reactive torque into a 13 torque track. The track is rigidly secured near its base to the 14 rig, transferring torque loads thereinto.
15The hereinabove described linkage type and other top 16 drive and track assemblies require substantial distance between 17 the track and the top drive to accommodate either the various 18 interconnecting means or the large physical size of the drive 19 mechanism. Clearance restrictions exist between the inside back of the derrick and the wellbore center. This limits the 21 application of the apparatus of the prior art to a small number 22 of derrick~ having large clearances.
23Although an increasing number of land rigs are being 24 manufactured or modified to accept conventional top drive units, to date all top drive installations described in the published 26 prior art have been permanent, to the best of applicant's ~ ,~
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1 knowledge. Because of the physical and mechanical limitations of 2 the top drive systems described in the prior art, a top drive 3 drilling system has not been available on an economical and 4 temporary basis for the vast majority of land drilling rigs and a substantially lesser number of offshore drilling rigs.
6 As stated, use of conventional top drives requires 7 substantial modifications to the rig. Generally, modifications 8 to a derrick will require structural re-certification.
9 Modifications are time consuming and expensive, and are not usually undertaken for a temporary installation. With all the 11 top drives described in the prior art, the purchase cost of a top 12 drive for a permanent installation in most rigs is not 13 economically justifiable when compared to conventional rotary 14 drilling equipment used in the same drilling application on a competitive basis.
16 With this background in mind, it was the objective of 17 the present invention to provide a compact, portable top drive 18 system that could be temporarily installed in existing drilling 19 rigs without structural modifications and without derating the derrick capacity.
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Sl~aRY OF TE~E INVENTION 211% 6 0 ~
2In designing and testing prototypes of the invention, 3it was concluded:
4 - that a top drive unit needed to be compact in order to fit within the wide range of derrick 6 types;
7 - that, while compact, the system needed to operate 8 with as high a drilling torque capacity as one 9 could manage;
- that there was a need to avoid transferring 11 torque loads into the relatively weak upper 12 derrick structure;
13 _ that there was a need to m;n;m;ze adding vertical 14 loads to the derrick, to avoid deration of the hook load capacity;
16 - that there was a need for a torque track that 17 could be easily installed on a temporary basis in 18 a derrick, without modification of the derrick;
19 - that it was desirable to improve pipe-handling capability for the top drive system;
21 - that it was desirable to provide an independent 22 power supply for the top drive, so that the top 23 drive could be incorporated without concern for 24 the nature of the rig's power supply; and 1 - that there was a need to so integrate the new top 2 drive system with an existing rig as to enable 3 quick conversion to top drive and quick return to 4 conventional rotary table operation, while still providing a portable system.
6 With these objectives in mind, an assembly was 7 developed for transmitting reactive torque loads from a top drive 8 unit ("top drive") to a rig in whose derrick the top drive is 9 suspended.
The assembly comprises a linearly exten~;ng, unitary, 11 substantially rigid, segmented torque track. The track is 12 mounted so as to extend vertically in the derrick along the major 13 part of the latter's length. The track is parallel with and 14 laterally offset from the wellbore, to allow the top drive and lS hoisting means to travel vertically in the derrick.
16 The track is formed of a plurality of sections which 17 are disengagably and rigidly joined end to end by suitable means.
18 The sections can thus be ass~embled section by section in the 19 derrick to create the unitary track. The track can be disassembled when desired into easily transportable sections.
21 The track is rigidly and disengagably secured by 22 connection means, located at its base, with the rig. More 23 particularly, a torque beam and clamps can be used to secure the 24 track rigidly to the lower, robust end of the derrick. The connection means serve to hold the track vertically in the 26 derrick and transmit reactive loads from the track to the rig.
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1 The track is otherwise free of rigid connection with the derrick.
2 Therefore it can twist axially or deflect laterally if 3 sufficiently loaded.
4 A tubular tor~ue bushing rigidly engages the track.
This bushing is adapted to slide longitudinally along the track 6 but it cannot rotate thereon. More particularly, the track is 7 preferably of box section and so is the bushing. The latter is 8 slid over the latter to lock them together and prevent relative 9 rotational movement. This rigid lock up of the b~h;ng and track ensures that reactive loads applied to the bushing are 11 transmitted to the track.
12 Linking means are provided which connect the top drive 13 housing and the bushing. The linking means function to rigidly 14 restrain the housing against rotation by tying it to the bl~-sh;ng and track. Preferably, the linking means is a rigid, elongate 16 torque frame, pivotally connected at its ends with the housing 17 and bl~sh;ng, so that it can pivot about horizontal axes (but not 18 vertical axes). The linking means can be said to be 19 "rotationally rigid". Preferably the linking means is angularly disposed between bl~sh;ng and housing, so that it will accommodate 21 lateral displacement of the latter away from the track, for a 22 purpose to be described.
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, , 1 The assembly as described embodies certain essential 2 features that are novel in combination. More particularly:
3 the linking assembly, consisting of torque frame 4 and torque bushing, is adapted to transmit both the torque and side reactive loads or forces 6 generated in the top drive housing, to the track;
7 and 8 the track is rigidly tied to the rig only at the 9 base of the track. Thus, reactive loads are not transmitted to the upper reaches of the derrick.
11 It is our belief that the side loads are small 12 and they are converted into torque loads in the 13 track. The free-to-twist track column transmits lg all of these torque loads downwardly to the lS bottom connection, for transmittal into the rig 16 structure.
17 This structural arrangement has enabled use of a relatively 18 slender and light track, which lends itself to portability.
19 In a preferred aspect, a plurality of hydraulic motors are coupled through gear means to rotate a vertical drive shaft 21 assembly that connects the drill string with the swivel and 22 hoisting means. This design solves a shortcoming of some prior 23 art top drives, which connect the drill string with the swivel 24 and hoisting means through a stout housing. The housing can now be lighter. Also the hydraulic motor and gear assembly is 26 compact in comparison to prior art electric power systems.
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1 In another preferred aspect, a separate portable 2 hydraulic power unit is used to power the top drive and its 3 components, rather than utilizing the rig's power means. The 4 power unit supplies hydraulic fluid to the top drive motors through a clad bundle of hoses suspended from the derrick.
6 In another preferred aspect, the bales and elevator of 7 the top drive are pivotally suspended from a collar carried by 8 the lower end of the drive shaft assembly. Linearly extendable 9 means (e.g. cylinders) are pivotally connected at their rear ends to the rear portion of the top drive housing and at their front 11 ends to the bales, for rotating the bales and elevator forwardly 12 into a horizontal plane. This enables the top drive to be set 13 down on the rig floor, which assists in disassembly.
14 In another preferred aspect, the pivotally connected torque frame is coupled with pivotally mounted cylinders 16 connected between the bllching and the housing. This arrangement 17 enables the top drive to be laterally displaced. In this way, 18 the top drive can make connections in the~mousehole~ of the rig.
19 Broadly stated, the invention relates to a portable top drive assembly for use with a drilling rig having an upstAn~;~g 21 derrick operatively aligned over a wellbore, said derrick 22 supporting hoisting means, a swivel and a drill string exten~;ng 23 into the wellbore, said top drive assembly comprising: a top 24 drive unit comprising a housing, a drive assembly supported by the housing, and a tubular drive shaft assembly extending 26 vertically through the housing and being connected with the drive 1 assembly for rotation thereby, said drive shaft assembly having 2 upper and lower ends and being connected at its lower end with 3 the drill string and at its upper end with the swivel for 4 suspension from the derrick by the hoisting means; the top drive S unit being operative to develop reactive side and torque loads in 6 the housing when the drive shaft rotates the drill string; and 7 apparatus for transmitting the reactive loads from the housing to 8 the rig comprising a linearly exten~;ng, substantially rigid 9 torque track ext~n~-ng vertically in the derrick along the major part of the derrick~s length, said track having upper and lower 11 ends, said track being parallel with and laterally offset from 12 the wellbore, said track being formed of sections joined end to 13 end, means for disengagably and rigidly connecting the track 14 sections end to end, means for rigidly connecting the track at its lower end with the rig so that reactive loads applied to the 16 track are transmitted therethrough to the rig and so that the 17 track is held upright in the derrick, the track otherwise being 18 free of rigid connection with the derrick so that it can twist 19 axially and deflect laterally relative to the derrick, a torque b~sh;ng rigidly engaging the track so that it can slide 21 therealong but cannot rotate thereon, said bushing being 22 operative to transmit reactive loads applied to it to the track, 23 and linking means, connecting the housing and the bushing, for 24 rigidly restr~;n;ng the housing against rotation relative to the bushing and track and for transmitting reactive side and torque 26 loads from the housing to the track.
,., - j~, BRIEF n~Sr~TPTION OF TE~E DRAWINGS 2118 6 0 8 2 Figure 1 provides a simplified side view of a 3 conventional land drilling rig having the portable top drive 4 system installed;
Figure 2 is a front view showing the top drive unit 6 (some detail omitted) suspended from a rig hoisting assembly;
7 Figure 3 is a side view of the top drive unit shown in 8 Figure 2;
9 Figure 4 is a front sectional view of the top drive unit as sectioned through its drive shaft axis;
11 Figure S is a detail sectional view of the gearbox and 12 drive shaft of Figure 4;
13 Figure 6 is a partial front view of the top drive unit, 14 detailing the pipe handling assembly in an unloaded state;
Figure 7 is a front view of the pipe handling assembly 16 of Figure 6 in the loaded state;
17 Figure 8 is an enlarged front view of the load collar 18 and load collar sub of Figures 6 and 7;
19 Figure 9 is a side view of the top drive system with the pipe handling assembly in a tilted orientation;
21 Figure 10 is a top view of the top drive system, 22 including the tilted bales and elevators;
23 Figure 11 is a side view of a three section torque 24 track assembly in a loosely articulated arrangement;
Figure 12a is a front sectional view of a disassembled 26 track section joint;
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1 Figure 12b is a front sectional view of the assembled 2 track section joint of Figure 12a, showing the joint in a 3 disengaged condition, with a phantom view of an articulated 4 positioning;
Figure 13 is a front sectional view of the track 6 section joint of Figure 12b in its final rigidified, engaged 7 form;
8 Figure 14 is a side view of the top drive unit, torque 9 bushing, torque track upper and lower connection means and torque beam;
11 Figure 15 is a top view of the torque track connection 12 means and torque beam according to Figure 14;
13 Figure 16 is a partial side view of the top drive unit, 14 detailing the backup wrench means sectioned through the drill string axis;
16 Figure 17 is a top sectional view of the backup wrench, 17 according to Figure 16, shown in a gripping state of a drill 18 joint;
19 Figure 18 is a side view of the top drive system in an extended orientation (pipe handling assembly omitted);
21 Figure 19 is a top view of the pivot link frame of 22 Figure 18;
23 Figure 20 is an alternate installation of the torque 24 track on a portable drilling rig;
Figure 21 is a 90 rotated top view of an alternate 26 torque beam used in the installation according to Figure 20;
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1 Figure 22 is a free body force diagram of the top drive 2 housing, pivoting link, and torque bushing demonstrating pure 3 side loading forces to the torque bushing assuming an infinitely 4 stiff drill string.
Figure 23 is a free body force diagram according to 6 Figure 22 in a substantially torque loaded condition having 7 recognised the flexible nature of the drill string.
8 DE~TTT~n n~S~RTPTION OF T~E PREFERRED EMBODIMENT
9 The present invention provides an improved portable top drive system for converting conventional kelly and rotary table 11 drilling rigs to top drive. As illustrated in Figure 1, a 12 conventional rig 1 has a rig sub-structure 2 positioned over a 13 wellbore 3. The sub-structure 2 has an opening 4 through which 14 a drill string 5 may extend downwards into the wellbore 3. The sub-structure 2 also usually has a mousehole opening 100 for use 16 in making connections. A derrick 6 stands above the rig sub-17 structure 2, operatively aligned relative to the wellbore 3, to 18 support the drill string 5 from hoisting means 7 shown in Figures 19 2 and 3. The hoisting means 7 comprises a crown block 8, cables 9, travelling block 10 and hook 11 and suspends a swivel 12.
21 Access to the rig is provided through a V-door opening 101 in one 22 side of the derrick 6.
1 A top drive unit 13 replaces a conventional elevator 2 and is suspended from the swivel 12. The swivel 12 is in turn 3 suspended from the travelling block 10 and hook 11, which may 4 lift and lower the top drive unit 13 in the derrick 6. The drill string 5 is suspended from the top drive unit 13. Drilling 6 rotation is imparted to the drill string 5 by the top drive unit 7 13.
8 The top drive unit 13 is hydraulically powered and is 9 supplied with actuating fluid via hoses contained within a clad hose bundle 15 ext~n~;ng from a portable power unit 16. Control 11 air and hydraulic lines 17, extending from a control panel 18, 12 and power hydraulic lines 19 are both provided within the hose 13 bundle 15. The hose bundle 15 is suspended from the derrick 6 to 14 permit free travel of the bundle throughout the range of top drive motion.
16 The control panel 18 is located on the rig floor 2 and 17 provides a combination of hydraulic, air and electric control of 18 top drive rotational speed (rpm), direction of rotation, pipe 19 handling and other features disclosed later in the description.
The control panel 18 also provides rpm limit and torque limit 21 controls for avoiding situations such as over-speed in case of 22 drill string failure and over-torquing of joints. The control 23 panel may be disconnected from the air, electric and hydraulic 24 lines 17 with quick connectors for shipping. The specific componentry referred to in the preceding two paragraphs is 26 conventional and will not be described in detail.
r 1 Referring to Figures 4 and 5, the top drive unit 13 2 comprises a structural housing 21, within which is positioned a 3 tubular drive shaft 22, hydraulic drive motors 23, and an oil 4 bath gearbox 24. The centrally located drive shaft 22 is vertically oriented and is adapted at its upper end 26 to thread 6 into the swivel 12, typically by threaded means directly or by an 7 adapter shaft (not shown). The hollow drive shaft 22 can 8 transport drilling fluids introduced through a fluid coupling 27 9 forming part of the swivel 12. Better viewed in Figure 5, the drive shaft 22 projects through the gearbox 24 and is fitted with 11 an external main gear 28. Four bi-directional rotary hydraulic 12 vane motors 23 are mounted to the gearbox 24, parallel to and 13 offset from the drive shaft 22, to rotationally drive pinion 14 gears 29 which mesh with the main gear 28, imparting the re~uired rotational torque. Low speed vane motors 23 are used to produce 16 high torque at low speed without the need for large, speed 17 reducing gearboxes and their associated bulk weight; this results 18 in a more compact, lighter top drive unit.
19 The housing 21 employs upper and lower thrust bearings 30, 31 on the drive shaft 22 to transmit the weight of the top 21 drive unit 13, and it's associated, attached components, to the 22 drive shaft 22 and thus to the hoisting means 7.
1 Referring to Figure 4, the drive shaft 22 supports the 2 drill string 5 through intermediary shafts comprising a load 3 collar sub 32 and a kelly saver sub 33. Together they make up a 4 drive shaft assembly. A kelly cock may be optionally included in combination with the saver sub 33. The lower end connection 38 6 of the saver sub 33 is adapted to thread into the upper end 7 connection 39 of the drill string 5 in use. The saver sub lower 8 end connection 38 is regularly connected and disconnected from 9 the upper end connection 39 of the drill string 5 during rig operation. The hoisting loads of the drill string 5 are 11 transferred through the savèr sub 33, the load collar sub 32 and 12 the drive shaft 22 to the hoisting means 7, avoiding loading of 13 the top drive housing 21. This enables use of a compact housing 14 21.
To prevent the drive shaft-to-load collar sub threaded 16 connections 34, 35 and the load collar sub-to-saver sub threaded 17 connections 36, 37 from unthreading during operation of the top 18 drive, locking clamps 40 are used.
19 It is desirable to suspend the weight of the pipe handling assembly 25 from the drive shaft assembly 205 and 21 hoisting means 7 when the assembly 25 is carrying the weight of 22 drill pipe. If this is accomplished, then the weight and size of 23 the top drive housing 21 can be reduced, contributing to 24 portability. The present assembly is therefore designed to suspend the pipe handling assembly 25 from the housing 21 when 26 its weight is below a predetermined amount and to transfer the 1 load to the drive shaft assembly 205 when the load is increased 2 by picking up drill string.
3 More particularly, having reference to Figures 4 and 4 6 - 9, the pipe handling assembly 25 comprises a load collar 41, elevator bales 42 and an elevator 43. The bales 42 are pivotally 6 suspended at their upper ends from the load collar 41 and thé
7 elevator 43 is pivotally suspended from the lower ends. All 8 three components are conventional in their structure.
9 The housing 21 has a hollow, cylindrical lower section 21a. A pair of parallel bars 46 are attached to the sidewall of 11 lower section 21a and extend horizontally on each side of the 12 load collar sub 32.
13 A cylindrical spring 45 is supported at its lower end 14 by the bars 46 and encircles the load collar sub 32 and extends vertically along part of its length. At its upper end, the 16 spring 45 is received by a ring 45a which supports the load 17 collar 41.
18 The load collar 41 is annular and forms an internal 19 bore 47. It is mounted around the load collar sub 32.
The load collar sub 32 has an enlarged diameter or 21 upset portion 48 adjacent its lower end. The horizontal bars 46 22 are located at the base of this upset portion 48.
23 The load collar 41 has a recessed load face 49 at its 24 lower end.
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1 If the spring 45 is fully expanded, it supports the 2 load collar 41 in an upraised position, as shown in Figure 6. In 3 this position, the load face 49 is spaced above the upper end 4 face 206 of the upset portion 48. However, the load collar 41 can slide downwardly along the sub 32 if the resistance of spring 6 45 is overcome. This downward travel by the load collar 41 is 7 terminated when its load face 49 contacts the end face 206 of the 8 upset portion 48. When the spring 45 is compressed in this 9 manner and the faces 49, 206 are in contact, the load collar 41 is in an engaged position with the drive shaft assembly 205.
11 This is shown in Figure 7.
12 In the upraised position, the weight of the empty pipe 13 handling assembly 25 is transmitted through the ring 45a, spring 14 45 and bars 46 to the housing 21. In the engaged portion, the weight of the loaded pipe handling assembly 25 is transmitted 16 from the load collar 41 directly to the drive shaft assembly 205.
17 Referring now to Figure 9, the pipe handling assembly 18 25 is shown to be angularly rotatable or tiltable from a normally 19 vertically downward orientation to a near horizontal position by the tilting sub-assembly 44. This tilting sub-assembly 44 21 comprises a pair of lift arms 50 pivotally connected at their 22 upper ends with the housing 2 by hole and pin means 52. The lift 23 arms 50 are also connected at their lower ends with the bales 42 24 by chains 53. Hydraulic cylinders 51 are pivotally connected at their inner ends by hole and pin means 55 with the housing 21 and 26 at their outer ends by hole and pin means 56 with the lift arms 1 ~
1 50. Extension of the hydraulic cylinders 51 can pivot the bales 2 42 upwardly and forwardly. This facilitates positioning the 3 elevator 43 as required for pipe handling and enables setting the 4 top drive unit 13 down on the rig floor 2.
The elevator 43 is conventional and has air powered 6 actuators 57 to automate opening and closing functions. For 7 safety reasons, the force developed by the air actuators 57 is 8 insufficient to open the elevators 43 when loaded with a drill g pipe.
The pipe handling assembly 25 provides improved pipe 11 handling, being capable of tilting the elevator 43 closer to the 12 derrickman, allowing him to avoid the dangerous reach-out over 13 space to pull back, capture or deliver pipe stands thereto during 14 racking-back and tripping operations. A tilt stop means 58 is provided to prevent over-rotation of the elevator 43 and 16 accidental contact with the derrick structure 6. The tilt stop 17 means 58 may be in the form of a limited length chain stop and 18 may be temporarily disabled to allow full rotation when setting 19 the top drive down.
Should a serious maintenance or breakdown situation 21 occur, or if very heavy drill, casing, tripping or fishing 22 operations are anticipated, the portable top drive unit 13 may be 23 set aside and the rig 1 may revert to conventional operation in 24 typically less than half an hour. With the tilt stop 58 disabled and the pipe handling assembly 25 fully tilted to nearly 26 hori70ntal, the top drive unit 13 may be set down on any strong ~ ~ ,., surface, such as the rig floor 2. The swivel 12 can be quickly unscrewed from the top drive 13, and the standard kelly may be reinstalled for re-implementation of the conventional rotary table and kelly operation.
A torque track 20 is mounted in the derrick 6 and extends vertically along the major part of the derrick's length.
The track 20 is a box-section and is substantially rigid. It is spaced rearwardly from the wellbore 3. It is rigidly connected at its lower end to the base of the derrick 6 and is suspended from the top of the derrick by a twistable, flexible cable 79.
The track 20 is therefore rigidly connected to the rig only at its lower end and is free to twist axially and deflect laterally.
The torque track 20 is connected with the housing 21 of the top drive unit 13 by an assembly comprising a torque bushing 59 and a linking means, specifically a torque frame 102.
The bushing 59 is tubular and box-like in section. It fits around and is slidable on the stationary track 20. Because of their box-like configurations, the bushing 59 rigidly engages the track 20 so that it cannot rotate thereon but will transmit reactive loads to it. Stated otherwise, the bushing 59 is rotationally rigid relative to the track 20.
The bushing 59 is internally face with ultra high molecular weight plastic having a low coefficient of friction, so that it slides easily on the track 20. It has a longitudinal slot 61 on one side to permit it to move past the connection means with the derrick 6.
The torque frame 102 is a rigid, flat, elongate member, 2 angularly disposed and pivotally connected at its ends by 3 horizontal pin and hole means 201, 202 with the housing 21 and 4 bl~.sh;ng 59. The frame 102 thus can pivot about horizontal axes, relative to the housing 21 and bushing 59, but it is restrained 6 by the b~.shlng from rotating relative to the track 20. Stated 7 otherwise, the torque frame is rotationally rigid relative to the 8 housing 21 and bushing 59.
9 The top drive unit 13 generates reactive side and torque loads when drilling. These loads are transmitted from the 11 housing 21, through the frame 102 and bushing 59, to the track 12 20. The track 20 transmits the loads to the rig 1 through its 13 rigid connection therewith.
14 The track 20, bushing 59 and frame 102 further cooperate to guide the top drive unit 13 as it travels in the 16 derrick 6.
17 The elongate form, angular positioning and pivoting 18 capability of the frame 102 enables the top drive unit 13 to be 19 displaced forwardly, so that it may be positioned over the mousehole or laid down on the rig floor.
21 l~e torque track 20 is assembled from a plurality of 22 sections of rectangular cross-section tubing, typically sized to 23 stAn~lArd oilfield drill pipe shipping lengths. In the particular 24 embodiment shown in Figure 11, three sections are depicted: a bottom section 63; a middle section 64; and a top section 65.
26 The bottom section 63 is fitted with a plurality of frequently .
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1 spaced mounting bolt holes 104 along its length to permit 2 adapting to the particular derrick 6 being fitted with the track 3 20. The middle and top sections 64, 65 may be identical and have 4 articulated assembly joints 66 mounted at each end, as seen in assembly Figures 12a, 12b and 13. The lower joint end of the top 6 section 65 cooperates with the matching upper joint end of the 7 middle section 64 to permit angular articulation during 8 installation, yet when the sections 64, 65 are placed in 9 collinear alignment they may be fitted together to form the linearly contiguous, unitary structural torque track 20. The 11 upper end of a cable 69 is fitted loosely through a first closing 12 plate 70 and is retained from slipping through with a button stop 13 71 at the cable end. The lower end of the cable 69 is similarly 14 loosely fitted through a J-lock fitting 72a and is retained with a button stop 73. The 1/8 turn J-lock 72a adapts to disengagably 16 connect the cable to a matching J-lock receiving fitting 72b on 17 a second closing plate 74. The cable is of a suitable length 18 that the track sections may articulate freely with a flexing of 19 the cable, yet is short enough to retract within the track when the sections are drawn together. A protuberance 75a ext~n~i ng 21 from the first closing plate 70 is adapted to fit into a matching 22 opening;75b in the second closing plate 74. The protuberance 23 engages the or~;n~ 75b until a bolting flange 75c contacts the 24 second closing plate 74 thereby aligning and stabilizing the sections together. Locking means 76 such as bolts are employed 26 to rigidly join the track sections 64, 65. The bottom section 63 1 is similarly joined to the middle section 64 to complete the 2 torque track 20 assembly.
3Referring to Figures 14 and 15, the torque track 20 is 4 secured to the derrick 6 with an upper and a lower connection means 77, 78. The upper connection means 77 comprises a cable 79 6 attaching the upper joint end of the top track section 65 to a 7 suitable cross-brace 80 at the crown of the derrick 6 with a 8 clamping means 81. The upper connection means 77 includes a 9 vertical adjusting means 77b, such as a turnbuckle, to provide limited vertical adjustment. The torque track 20 is suspended by 11 this upper connection means 77 which is capable of stabilizing 12 horizontal movement of the torque track and yet freely rotates 13 when subjected to torque loading. The lower connection means 78 14 comprises a torque arm 82a connected to and projecting laterally from the torque track 20. The torque arm 82a may be connected 16 using any of a plurality of bolting holes (not shown) formed 17 along the track, to adapt to variable geometry of different 18 derricks 6. A torque beam 82b is connected to the torque arm to 19 connect to suitable bracing 83 on the derrick 6 near its robust base where reactive drilling torques may safely be absorbed. The 21 torque track 20 is designed with sufficient torsional rigidity to 22 transmit the full reactive drilling torque to the rigid lower 23 connection means 78 and into the substructure of the drilling rig 24 1. The torque beam 82b is rigidly attached to the bracing 83 on the derrick 6 with a clamping means 84a which permits connections 26 to be made without need for welding or other structural .~,.
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1 modifications to be made to the derrick 6. The torque arm is 2 similarly rigidly attached to the torque beam with a clamping 3 means 84b. The clamping means 84a, 84b permit adjustments to re-4 align the torque track 20 to the wellbore as required.
The mechanism that permits the torque track to absorb 6 the reactive loads as substantially torque and to prevent side 7 loading of the upper structure of the derrick is not immediately 8 apparent.
9 Referring to Figure 22, a free body force diagram of the top drive housing 21, pivoting frame 102, and torque bushing 11 59 is shown. The top drive housing 21 is depicted as imparting 12 a CW torque Tl to the drill string 5. The drill string resists 13 the rotation and results in a CCW couple Cl into the frame.
14 Assume for the moment, that the drill string is infinitely stiff.The frame acts as a moment arm which attempts to rotate around 16 the drill string. The moment arm will impose purely side loading 17 ga into the torque b~)sh;ng 59 and in turn into the torque track 18 20. An equal and opposite balancing load Sl then exists in the 19 moment arm. To prevent free rotation of the rigid frame around the track due to the balancing force gl, a reactive side load Rl 21 must exist on the drill string. Similarly, a reactive side load 22 R~ must exist at the track. Should the assumption of the stiff 23 drill string be true, high side loading of the torque track would24 result. High side loads could deflect the track significantly and impose loading to the top of the derrick which is contrary to 26 the objective.
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1 Referring to Figure 23, the drill string is found to 2 be, not infinitely stiff, but is actually weak in side loading.
3 If Rl is then essentially zero, the moment arm rotates 4 essentially freely and deflects an amount dl, typically a couple of inches. The track is strong in side loading and deflects only 6 a very small amount d2 to balance the small load Rl.
7 The track must rotate with the moment arm or frame, 8 being rigidly fixed thereto. The track has significant torsional 9 rigidity and resists this rotation. This resistance manifests as a couple C2 and permits a small twist or rotation of the track.
11 The reactive side load R2 on the track ~im;n; shes as the drill 12 string deflects, the load being absorbed in the couple C2. The 13 side loading Sl has thus been substantially converted to a 14 reactive torque 10A~; ng C2 into the track.
Several factors contribute to the drill string 5 being 16 weak and permitting the conversion of side loads to torque 17 loading. The drill string is normally long in length, has a 18 relatively small mom nt of inertia and it extends down through a 19 large rig-floor opening into the wellbore which offers little support. The drill string 5 is connected at its upper end to the 21 top drive unit 13 which is connected to the travelling block 10.
22 The travelling block is hung from the crown with cables 9 which 23 are not normally capable of sust~;n;ng side loads.
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1 Two extreme cases exist which interfere with the side-2 to-torque load conversion mechanism. When the top drive is 3 positioned near the rig floor 2, and particularly when slips are 4 engaged at the rotary table, the drill string 5 is stiffened and cannot deflect. The pivoting frame 102 acts as a moment arm and 6 transfers pure side loading to the torque track 20. This extreme 7 case is adequately compensated by the close proximity of the 8 strong torque arm 82a and torque beam 82b connection, absorbing 9 side loads without subjecting the upper part of the derrick to reactive loading. The second case occurs when the top drive is 11 positioned at the top of the derrick 6. Theoretically, one could 12 shorten the length of the cable 9 to zero, thus stiffening the 13 drill string. This situation is highly unlikely to occur and in 14 the worst case would result in reactive load sharing between the torque track 20 and the derrick 6.
16 Operations other than drilling place special load 17 conditions on the torque track 20. Lifting of heavy loads from 18 the V-door 101 can place unusual side loads on the torque track 19 20, deflecting it away from the derrick 6. Of particular concern is the rebound effect when the load is released, potentially 21 permitting the torque track to strike the structure of the 22 derrick, often located ;mme~ately adjacent the track. In the 23 worst case, if the torque bushing 59 is moving at that instant, 24 it can collide with the derrick 6, potentially damaging both the derrick and the bushing.
1 As shown in Figure 14, it is preferable to install a 2 steadying means such as turnbuckles 105, connected between the 3 derrick and torque track at vertically spaced points. Bars 106 4 having a plurality of connecting sites are attached to the torque track 20. Connection of the turnbuckle 105 to each bar 106 is 6 loose enough to permit reactive load movement but is sufficiently 7 rigid to prevent contact of the torque bushing 59 with the 8 derrick 6. Stated otherwise, the connection prevents the track 9 from moving toward or away from the back of the derrick but the connection is loose enough to allow the track to move sideways 11 and most importantly is loose enough that the connection cannot 12 transmit any torque.
13 Referring to Figures 16 and 17, at an elevation near 14 and below the lower end 38 of the saver sub 33, a backup wrench assembly 85 is provided comprising opposing rotation drill string 16 tongs 86 having stAn~rd oilfield tong jaw dies 87. Individual 17 hydraulic actuating means 88 are provided to cause the tong jaws 18 to hold the drill pipe 5 stationary while the drive shaft 22 is 19 appropriately rotated to connect or disconnect the saver sub joint 38, 39 thereto. The wrench assembly 85 makes it possible 21 to make or break the tool joint at any position in the derrick.
22 The wrench ~ssembly 85 is secured to the lower portion of the top 23 drive housing 21 with a spring mount means 89. When disengaging 24 a drill pipe 5 from the saver sub 33, the wrench assembly is positioned to engage the top of the pipe. As the saver sub is 26 screwed out of the drill pipe 5, the springs 89 deflect, ~ ~. ~.
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,, 1 permitting both the pipe 5 and the wrench assembly 85 to be moved 2 down by the pitch action of the threads.
3 A hydraulic cylinder 95 is pivotally connected at its 4 en~s by horizontal pin and hole means 203, 204 with the torque bushing 59 and top drive housing 21. Extension of the cylinder 6 90 will shift the top drive unit 13 forwardly; the pivoting frame 7 102 accommodates this movement. The top drive unit 13 can thus 8 be biased to an alternate position, such as over the mousehole 9 100.
It may not be feasible to locate the torque track 20 at the 11 back of the derrick 6. This can occur in the case of a portable 12 rig 103 having a le~n;ng derrick 6, where an obstacle free path 13 is not available from the rig floor 2 to the crown of the derrick 14 (Figures 20 and 21). In this case, the torque track 20 may be installed at right angles from the wellbore 3 and mousehole 100 16 alignment. The torque track 20 is suspended from the crown brace 17 80 with the upper connection means 77 as previously described, 18 but the lower connection means 78 is provided by a telescoping 19 torque beam assembly 96, whereby the first end of the beam 97 is secured to the robust base of the derrick 6 with the clamping 21 means 84 and the -s~con~ end 98 is moveable with respect to the 22 first and i8 pivotally connected to the torque track 20. An 23 exten~ing and retracting means 99 is provided to extend the 24 second end 98 with respect to the first end, resulting in a pivoting of the entire track 20, from the crown bracing 80, 26 thereby ext~n~ing the top drive unit 13 from a position over the l~ ~
21186~8 1 wellbore 3 to an alternate position such as over the mousehole 2 100.
3 With the ~extend" feature, several advantages in pipe 4 handling and efficiency are realized. The extend feature permits the mousehole, offset from the wellbore, to be drilled by the top 6 drive. It is possible to make up drill pipe connections at the 7 mousehole with the joint connection at the rig floor, at eye 8 level. Stands of drill pipe can be made up over the mousehole, 9 improving drilling efficiency. When drilling, the top drive may drill to the floor and, using a combination of extend and the 11 tilt elevator, one can simultaneously pick up a new length of 12 pipe from the V-door. The extend feature may also be used to 13 further assist the derrickman in handling drill collars, as the 14 bales and elevator can then bring the particularly heavy collars closer.
It has previously been common in well drilling to 6 impart rotational drilling or hoisting forces to a drill string 7 using a top drive unit mounted to a guide track extending 8 upwardly within a rig derrick. These top drive units use either 9 electric or hydraulic power. The units are generally large and are designed primarily for offshore rigs, although they have been 11 installed in land rigs.
12 In prior applications, the rig derrick has had to be 13 modified to some degree, usually through welding, to be able to 14 accept the size of the machine, the track on which the top drive unit travels, and to be able to accept the torque imparted to the 16 derrick from the top drive unit through the track. In some 17 installations, the derrick has had to be extended to accommodate 18 the top drive unit. In most cases, the rig's travelling blocks 19 and/or rotary drilling swivel have had to be replaced or modified in order to work with the top drive unit.
21 Top drive implementation requires a reactive torque 22 absorbing means. This is provided by a vertical guide track or 23 a tensioned cabIe secured to the derrick. The tensioned cable 24 puts high vertical loads on the derrick, forcing a deration of the hook load capacity. Guide tracks have generally been secured 2~1860~
1 to the derrick in a manner such that significant reactive torque 2 is transmitted to the derrick structure along its length, which 3 has generally been designed for heavy vertical and only nominal 4 torque loads; this has required structural modifications to compensate.
6One type of reactive torque absorbing means that has 7 been used specifically to reduce reactive torque loads on the 8derrick is disclosed in United States patent No. 2,998,084, 9 issued to Johnson et al. This patent teaches a top drive and track having an interconnecting pivoting linkage apparatus. The 11 linkage pivots about vertical axes; it is unable to transfer side 12 loading and transmits pure rotational reactive torque into a 13 torque track. The track is rigidly secured near its base to the 14 rig, transferring torque loads thereinto.
15The hereinabove described linkage type and other top 16 drive and track assemblies require substantial distance between 17 the track and the top drive to accommodate either the various 18 interconnecting means or the large physical size of the drive 19 mechanism. Clearance restrictions exist between the inside back of the derrick and the wellbore center. This limits the 21 application of the apparatus of the prior art to a small number 22 of derrick~ having large clearances.
23Although an increasing number of land rigs are being 24 manufactured or modified to accept conventional top drive units, to date all top drive installations described in the published 26 prior art have been permanent, to the best of applicant's ~ ,~
211860~
1 knowledge. Because of the physical and mechanical limitations of 2 the top drive systems described in the prior art, a top drive 3 drilling system has not been available on an economical and 4 temporary basis for the vast majority of land drilling rigs and a substantially lesser number of offshore drilling rigs.
6 As stated, use of conventional top drives requires 7 substantial modifications to the rig. Generally, modifications 8 to a derrick will require structural re-certification.
9 Modifications are time consuming and expensive, and are not usually undertaken for a temporary installation. With all the 11 top drives described in the prior art, the purchase cost of a top 12 drive for a permanent installation in most rigs is not 13 economically justifiable when compared to conventional rotary 14 drilling equipment used in the same drilling application on a competitive basis.
16 With this background in mind, it was the objective of 17 the present invention to provide a compact, portable top drive 18 system that could be temporarily installed in existing drilling 19 rigs without structural modifications and without derating the derrick capacity.
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Sl~aRY OF TE~E INVENTION 211% 6 0 ~
2In designing and testing prototypes of the invention, 3it was concluded:
4 - that a top drive unit needed to be compact in order to fit within the wide range of derrick 6 types;
7 - that, while compact, the system needed to operate 8 with as high a drilling torque capacity as one 9 could manage;
- that there was a need to avoid transferring 11 torque loads into the relatively weak upper 12 derrick structure;
13 _ that there was a need to m;n;m;ze adding vertical 14 loads to the derrick, to avoid deration of the hook load capacity;
16 - that there was a need for a torque track that 17 could be easily installed on a temporary basis in 18 a derrick, without modification of the derrick;
19 - that it was desirable to improve pipe-handling capability for the top drive system;
21 - that it was desirable to provide an independent 22 power supply for the top drive, so that the top 23 drive could be incorporated without concern for 24 the nature of the rig's power supply; and 1 - that there was a need to so integrate the new top 2 drive system with an existing rig as to enable 3 quick conversion to top drive and quick return to 4 conventional rotary table operation, while still providing a portable system.
6 With these objectives in mind, an assembly was 7 developed for transmitting reactive torque loads from a top drive 8 unit ("top drive") to a rig in whose derrick the top drive is 9 suspended.
The assembly comprises a linearly exten~;ng, unitary, 11 substantially rigid, segmented torque track. The track is 12 mounted so as to extend vertically in the derrick along the major 13 part of the latter's length. The track is parallel with and 14 laterally offset from the wellbore, to allow the top drive and lS hoisting means to travel vertically in the derrick.
16 The track is formed of a plurality of sections which 17 are disengagably and rigidly joined end to end by suitable means.
18 The sections can thus be ass~embled section by section in the 19 derrick to create the unitary track. The track can be disassembled when desired into easily transportable sections.
21 The track is rigidly and disengagably secured by 22 connection means, located at its base, with the rig. More 23 particularly, a torque beam and clamps can be used to secure the 24 track rigidly to the lower, robust end of the derrick. The connection means serve to hold the track vertically in the 26 derrick and transmit reactive loads from the track to the rig.
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1 The track is otherwise free of rigid connection with the derrick.
2 Therefore it can twist axially or deflect laterally if 3 sufficiently loaded.
4 A tubular tor~ue bushing rigidly engages the track.
This bushing is adapted to slide longitudinally along the track 6 but it cannot rotate thereon. More particularly, the track is 7 preferably of box section and so is the bushing. The latter is 8 slid over the latter to lock them together and prevent relative 9 rotational movement. This rigid lock up of the b~h;ng and track ensures that reactive loads applied to the bushing are 11 transmitted to the track.
12 Linking means are provided which connect the top drive 13 housing and the bushing. The linking means function to rigidly 14 restrain the housing against rotation by tying it to the bl~-sh;ng and track. Preferably, the linking means is a rigid, elongate 16 torque frame, pivotally connected at its ends with the housing 17 and bl~sh;ng, so that it can pivot about horizontal axes (but not 18 vertical axes). The linking means can be said to be 19 "rotationally rigid". Preferably the linking means is angularly disposed between bl~sh;ng and housing, so that it will accommodate 21 lateral displacement of the latter away from the track, for a 22 purpose to be described.
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, , 1 The assembly as described embodies certain essential 2 features that are novel in combination. More particularly:
3 the linking assembly, consisting of torque frame 4 and torque bushing, is adapted to transmit both the torque and side reactive loads or forces 6 generated in the top drive housing, to the track;
7 and 8 the track is rigidly tied to the rig only at the 9 base of the track. Thus, reactive loads are not transmitted to the upper reaches of the derrick.
11 It is our belief that the side loads are small 12 and they are converted into torque loads in the 13 track. The free-to-twist track column transmits lg all of these torque loads downwardly to the lS bottom connection, for transmittal into the rig 16 structure.
17 This structural arrangement has enabled use of a relatively 18 slender and light track, which lends itself to portability.
19 In a preferred aspect, a plurality of hydraulic motors are coupled through gear means to rotate a vertical drive shaft 21 assembly that connects the drill string with the swivel and 22 hoisting means. This design solves a shortcoming of some prior 23 art top drives, which connect the drill string with the swivel 24 and hoisting means through a stout housing. The housing can now be lighter. Also the hydraulic motor and gear assembly is 26 compact in comparison to prior art electric power systems.
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1 In another preferred aspect, a separate portable 2 hydraulic power unit is used to power the top drive and its 3 components, rather than utilizing the rig's power means. The 4 power unit supplies hydraulic fluid to the top drive motors through a clad bundle of hoses suspended from the derrick.
6 In another preferred aspect, the bales and elevator of 7 the top drive are pivotally suspended from a collar carried by 8 the lower end of the drive shaft assembly. Linearly extendable 9 means (e.g. cylinders) are pivotally connected at their rear ends to the rear portion of the top drive housing and at their front 11 ends to the bales, for rotating the bales and elevator forwardly 12 into a horizontal plane. This enables the top drive to be set 13 down on the rig floor, which assists in disassembly.
14 In another preferred aspect, the pivotally connected torque frame is coupled with pivotally mounted cylinders 16 connected between the bllching and the housing. This arrangement 17 enables the top drive to be laterally displaced. In this way, 18 the top drive can make connections in the~mousehole~ of the rig.
19 Broadly stated, the invention relates to a portable top drive assembly for use with a drilling rig having an upstAn~;~g 21 derrick operatively aligned over a wellbore, said derrick 22 supporting hoisting means, a swivel and a drill string exten~;ng 23 into the wellbore, said top drive assembly comprising: a top 24 drive unit comprising a housing, a drive assembly supported by the housing, and a tubular drive shaft assembly extending 26 vertically through the housing and being connected with the drive 1 assembly for rotation thereby, said drive shaft assembly having 2 upper and lower ends and being connected at its lower end with 3 the drill string and at its upper end with the swivel for 4 suspension from the derrick by the hoisting means; the top drive S unit being operative to develop reactive side and torque loads in 6 the housing when the drive shaft rotates the drill string; and 7 apparatus for transmitting the reactive loads from the housing to 8 the rig comprising a linearly exten~;ng, substantially rigid 9 torque track ext~n~-ng vertically in the derrick along the major part of the derrick~s length, said track having upper and lower 11 ends, said track being parallel with and laterally offset from 12 the wellbore, said track being formed of sections joined end to 13 end, means for disengagably and rigidly connecting the track 14 sections end to end, means for rigidly connecting the track at its lower end with the rig so that reactive loads applied to the 16 track are transmitted therethrough to the rig and so that the 17 track is held upright in the derrick, the track otherwise being 18 free of rigid connection with the derrick so that it can twist 19 axially and deflect laterally relative to the derrick, a torque b~sh;ng rigidly engaging the track so that it can slide 21 therealong but cannot rotate thereon, said bushing being 22 operative to transmit reactive loads applied to it to the track, 23 and linking means, connecting the housing and the bushing, for 24 rigidly restr~;n;ng the housing against rotation relative to the bushing and track and for transmitting reactive side and torque 26 loads from the housing to the track.
,., - j~, BRIEF n~Sr~TPTION OF TE~E DRAWINGS 2118 6 0 8 2 Figure 1 provides a simplified side view of a 3 conventional land drilling rig having the portable top drive 4 system installed;
Figure 2 is a front view showing the top drive unit 6 (some detail omitted) suspended from a rig hoisting assembly;
7 Figure 3 is a side view of the top drive unit shown in 8 Figure 2;
9 Figure 4 is a front sectional view of the top drive unit as sectioned through its drive shaft axis;
11 Figure S is a detail sectional view of the gearbox and 12 drive shaft of Figure 4;
13 Figure 6 is a partial front view of the top drive unit, 14 detailing the pipe handling assembly in an unloaded state;
Figure 7 is a front view of the pipe handling assembly 16 of Figure 6 in the loaded state;
17 Figure 8 is an enlarged front view of the load collar 18 and load collar sub of Figures 6 and 7;
19 Figure 9 is a side view of the top drive system with the pipe handling assembly in a tilted orientation;
21 Figure 10 is a top view of the top drive system, 22 including the tilted bales and elevators;
23 Figure 11 is a side view of a three section torque 24 track assembly in a loosely articulated arrangement;
Figure 12a is a front sectional view of a disassembled 26 track section joint;
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1 Figure 12b is a front sectional view of the assembled 2 track section joint of Figure 12a, showing the joint in a 3 disengaged condition, with a phantom view of an articulated 4 positioning;
Figure 13 is a front sectional view of the track 6 section joint of Figure 12b in its final rigidified, engaged 7 form;
8 Figure 14 is a side view of the top drive unit, torque 9 bushing, torque track upper and lower connection means and torque beam;
11 Figure 15 is a top view of the torque track connection 12 means and torque beam according to Figure 14;
13 Figure 16 is a partial side view of the top drive unit, 14 detailing the backup wrench means sectioned through the drill string axis;
16 Figure 17 is a top sectional view of the backup wrench, 17 according to Figure 16, shown in a gripping state of a drill 18 joint;
19 Figure 18 is a side view of the top drive system in an extended orientation (pipe handling assembly omitted);
21 Figure 19 is a top view of the pivot link frame of 22 Figure 18;
23 Figure 20 is an alternate installation of the torque 24 track on a portable drilling rig;
Figure 21 is a 90 rotated top view of an alternate 26 torque beam used in the installation according to Figure 20;
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1 Figure 22 is a free body force diagram of the top drive 2 housing, pivoting link, and torque bushing demonstrating pure 3 side loading forces to the torque bushing assuming an infinitely 4 stiff drill string.
Figure 23 is a free body force diagram according to 6 Figure 22 in a substantially torque loaded condition having 7 recognised the flexible nature of the drill string.
8 DE~TTT~n n~S~RTPTION OF T~E PREFERRED EMBODIMENT
9 The present invention provides an improved portable top drive system for converting conventional kelly and rotary table 11 drilling rigs to top drive. As illustrated in Figure 1, a 12 conventional rig 1 has a rig sub-structure 2 positioned over a 13 wellbore 3. The sub-structure 2 has an opening 4 through which 14 a drill string 5 may extend downwards into the wellbore 3. The sub-structure 2 also usually has a mousehole opening 100 for use 16 in making connections. A derrick 6 stands above the rig sub-17 structure 2, operatively aligned relative to the wellbore 3, to 18 support the drill string 5 from hoisting means 7 shown in Figures 19 2 and 3. The hoisting means 7 comprises a crown block 8, cables 9, travelling block 10 and hook 11 and suspends a swivel 12.
21 Access to the rig is provided through a V-door opening 101 in one 22 side of the derrick 6.
1 A top drive unit 13 replaces a conventional elevator 2 and is suspended from the swivel 12. The swivel 12 is in turn 3 suspended from the travelling block 10 and hook 11, which may 4 lift and lower the top drive unit 13 in the derrick 6. The drill string 5 is suspended from the top drive unit 13. Drilling 6 rotation is imparted to the drill string 5 by the top drive unit 7 13.
8 The top drive unit 13 is hydraulically powered and is 9 supplied with actuating fluid via hoses contained within a clad hose bundle 15 ext~n~;ng from a portable power unit 16. Control 11 air and hydraulic lines 17, extending from a control panel 18, 12 and power hydraulic lines 19 are both provided within the hose 13 bundle 15. The hose bundle 15 is suspended from the derrick 6 to 14 permit free travel of the bundle throughout the range of top drive motion.
16 The control panel 18 is located on the rig floor 2 and 17 provides a combination of hydraulic, air and electric control of 18 top drive rotational speed (rpm), direction of rotation, pipe 19 handling and other features disclosed later in the description.
The control panel 18 also provides rpm limit and torque limit 21 controls for avoiding situations such as over-speed in case of 22 drill string failure and over-torquing of joints. The control 23 panel may be disconnected from the air, electric and hydraulic 24 lines 17 with quick connectors for shipping. The specific componentry referred to in the preceding two paragraphs is 26 conventional and will not be described in detail.
r 1 Referring to Figures 4 and 5, the top drive unit 13 2 comprises a structural housing 21, within which is positioned a 3 tubular drive shaft 22, hydraulic drive motors 23, and an oil 4 bath gearbox 24. The centrally located drive shaft 22 is vertically oriented and is adapted at its upper end 26 to thread 6 into the swivel 12, typically by threaded means directly or by an 7 adapter shaft (not shown). The hollow drive shaft 22 can 8 transport drilling fluids introduced through a fluid coupling 27 9 forming part of the swivel 12. Better viewed in Figure 5, the drive shaft 22 projects through the gearbox 24 and is fitted with 11 an external main gear 28. Four bi-directional rotary hydraulic 12 vane motors 23 are mounted to the gearbox 24, parallel to and 13 offset from the drive shaft 22, to rotationally drive pinion 14 gears 29 which mesh with the main gear 28, imparting the re~uired rotational torque. Low speed vane motors 23 are used to produce 16 high torque at low speed without the need for large, speed 17 reducing gearboxes and their associated bulk weight; this results 18 in a more compact, lighter top drive unit.
19 The housing 21 employs upper and lower thrust bearings 30, 31 on the drive shaft 22 to transmit the weight of the top 21 drive unit 13, and it's associated, attached components, to the 22 drive shaft 22 and thus to the hoisting means 7.
1 Referring to Figure 4, the drive shaft 22 supports the 2 drill string 5 through intermediary shafts comprising a load 3 collar sub 32 and a kelly saver sub 33. Together they make up a 4 drive shaft assembly. A kelly cock may be optionally included in combination with the saver sub 33. The lower end connection 38 6 of the saver sub 33 is adapted to thread into the upper end 7 connection 39 of the drill string 5 in use. The saver sub lower 8 end connection 38 is regularly connected and disconnected from 9 the upper end connection 39 of the drill string 5 during rig operation. The hoisting loads of the drill string 5 are 11 transferred through the savèr sub 33, the load collar sub 32 and 12 the drive shaft 22 to the hoisting means 7, avoiding loading of 13 the top drive housing 21. This enables use of a compact housing 14 21.
To prevent the drive shaft-to-load collar sub threaded 16 connections 34, 35 and the load collar sub-to-saver sub threaded 17 connections 36, 37 from unthreading during operation of the top 18 drive, locking clamps 40 are used.
19 It is desirable to suspend the weight of the pipe handling assembly 25 from the drive shaft assembly 205 and 21 hoisting means 7 when the assembly 25 is carrying the weight of 22 drill pipe. If this is accomplished, then the weight and size of 23 the top drive housing 21 can be reduced, contributing to 24 portability. The present assembly is therefore designed to suspend the pipe handling assembly 25 from the housing 21 when 26 its weight is below a predetermined amount and to transfer the 1 load to the drive shaft assembly 205 when the load is increased 2 by picking up drill string.
3 More particularly, having reference to Figures 4 and 4 6 - 9, the pipe handling assembly 25 comprises a load collar 41, elevator bales 42 and an elevator 43. The bales 42 are pivotally 6 suspended at their upper ends from the load collar 41 and thé
7 elevator 43 is pivotally suspended from the lower ends. All 8 three components are conventional in their structure.
9 The housing 21 has a hollow, cylindrical lower section 21a. A pair of parallel bars 46 are attached to the sidewall of 11 lower section 21a and extend horizontally on each side of the 12 load collar sub 32.
13 A cylindrical spring 45 is supported at its lower end 14 by the bars 46 and encircles the load collar sub 32 and extends vertically along part of its length. At its upper end, the 16 spring 45 is received by a ring 45a which supports the load 17 collar 41.
18 The load collar 41 is annular and forms an internal 19 bore 47. It is mounted around the load collar sub 32.
The load collar sub 32 has an enlarged diameter or 21 upset portion 48 adjacent its lower end. The horizontal bars 46 22 are located at the base of this upset portion 48.
23 The load collar 41 has a recessed load face 49 at its 24 lower end.
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1 If the spring 45 is fully expanded, it supports the 2 load collar 41 in an upraised position, as shown in Figure 6. In 3 this position, the load face 49 is spaced above the upper end 4 face 206 of the upset portion 48. However, the load collar 41 can slide downwardly along the sub 32 if the resistance of spring 6 45 is overcome. This downward travel by the load collar 41 is 7 terminated when its load face 49 contacts the end face 206 of the 8 upset portion 48. When the spring 45 is compressed in this 9 manner and the faces 49, 206 are in contact, the load collar 41 is in an engaged position with the drive shaft assembly 205.
11 This is shown in Figure 7.
12 In the upraised position, the weight of the empty pipe 13 handling assembly 25 is transmitted through the ring 45a, spring 14 45 and bars 46 to the housing 21. In the engaged portion, the weight of the loaded pipe handling assembly 25 is transmitted 16 from the load collar 41 directly to the drive shaft assembly 205.
17 Referring now to Figure 9, the pipe handling assembly 18 25 is shown to be angularly rotatable or tiltable from a normally 19 vertically downward orientation to a near horizontal position by the tilting sub-assembly 44. This tilting sub-assembly 44 21 comprises a pair of lift arms 50 pivotally connected at their 22 upper ends with the housing 2 by hole and pin means 52. The lift 23 arms 50 are also connected at their lower ends with the bales 42 24 by chains 53. Hydraulic cylinders 51 are pivotally connected at their inner ends by hole and pin means 55 with the housing 21 and 26 at their outer ends by hole and pin means 56 with the lift arms 1 ~
1 50. Extension of the hydraulic cylinders 51 can pivot the bales 2 42 upwardly and forwardly. This facilitates positioning the 3 elevator 43 as required for pipe handling and enables setting the 4 top drive unit 13 down on the rig floor 2.
The elevator 43 is conventional and has air powered 6 actuators 57 to automate opening and closing functions. For 7 safety reasons, the force developed by the air actuators 57 is 8 insufficient to open the elevators 43 when loaded with a drill g pipe.
The pipe handling assembly 25 provides improved pipe 11 handling, being capable of tilting the elevator 43 closer to the 12 derrickman, allowing him to avoid the dangerous reach-out over 13 space to pull back, capture or deliver pipe stands thereto during 14 racking-back and tripping operations. A tilt stop means 58 is provided to prevent over-rotation of the elevator 43 and 16 accidental contact with the derrick structure 6. The tilt stop 17 means 58 may be in the form of a limited length chain stop and 18 may be temporarily disabled to allow full rotation when setting 19 the top drive down.
Should a serious maintenance or breakdown situation 21 occur, or if very heavy drill, casing, tripping or fishing 22 operations are anticipated, the portable top drive unit 13 may be 23 set aside and the rig 1 may revert to conventional operation in 24 typically less than half an hour. With the tilt stop 58 disabled and the pipe handling assembly 25 fully tilted to nearly 26 hori70ntal, the top drive unit 13 may be set down on any strong ~ ~ ,., surface, such as the rig floor 2. The swivel 12 can be quickly unscrewed from the top drive 13, and the standard kelly may be reinstalled for re-implementation of the conventional rotary table and kelly operation.
A torque track 20 is mounted in the derrick 6 and extends vertically along the major part of the derrick's length.
The track 20 is a box-section and is substantially rigid. It is spaced rearwardly from the wellbore 3. It is rigidly connected at its lower end to the base of the derrick 6 and is suspended from the top of the derrick by a twistable, flexible cable 79.
The track 20 is therefore rigidly connected to the rig only at its lower end and is free to twist axially and deflect laterally.
The torque track 20 is connected with the housing 21 of the top drive unit 13 by an assembly comprising a torque bushing 59 and a linking means, specifically a torque frame 102.
The bushing 59 is tubular and box-like in section. It fits around and is slidable on the stationary track 20. Because of their box-like configurations, the bushing 59 rigidly engages the track 20 so that it cannot rotate thereon but will transmit reactive loads to it. Stated otherwise, the bushing 59 is rotationally rigid relative to the track 20.
The bushing 59 is internally face with ultra high molecular weight plastic having a low coefficient of friction, so that it slides easily on the track 20. It has a longitudinal slot 61 on one side to permit it to move past the connection means with the derrick 6.
The torque frame 102 is a rigid, flat, elongate member, 2 angularly disposed and pivotally connected at its ends by 3 horizontal pin and hole means 201, 202 with the housing 21 and 4 bl~.sh;ng 59. The frame 102 thus can pivot about horizontal axes, relative to the housing 21 and bushing 59, but it is restrained 6 by the b~.shlng from rotating relative to the track 20. Stated 7 otherwise, the torque frame is rotationally rigid relative to the 8 housing 21 and bushing 59.
9 The top drive unit 13 generates reactive side and torque loads when drilling. These loads are transmitted from the 11 housing 21, through the frame 102 and bushing 59, to the track 12 20. The track 20 transmits the loads to the rig 1 through its 13 rigid connection therewith.
14 The track 20, bushing 59 and frame 102 further cooperate to guide the top drive unit 13 as it travels in the 16 derrick 6.
17 The elongate form, angular positioning and pivoting 18 capability of the frame 102 enables the top drive unit 13 to be 19 displaced forwardly, so that it may be positioned over the mousehole or laid down on the rig floor.
21 l~e torque track 20 is assembled from a plurality of 22 sections of rectangular cross-section tubing, typically sized to 23 stAn~lArd oilfield drill pipe shipping lengths. In the particular 24 embodiment shown in Figure 11, three sections are depicted: a bottom section 63; a middle section 64; and a top section 65.
26 The bottom section 63 is fitted with a plurality of frequently .
. ~,,,~
1 spaced mounting bolt holes 104 along its length to permit 2 adapting to the particular derrick 6 being fitted with the track 3 20. The middle and top sections 64, 65 may be identical and have 4 articulated assembly joints 66 mounted at each end, as seen in assembly Figures 12a, 12b and 13. The lower joint end of the top 6 section 65 cooperates with the matching upper joint end of the 7 middle section 64 to permit angular articulation during 8 installation, yet when the sections 64, 65 are placed in 9 collinear alignment they may be fitted together to form the linearly contiguous, unitary structural torque track 20. The 11 upper end of a cable 69 is fitted loosely through a first closing 12 plate 70 and is retained from slipping through with a button stop 13 71 at the cable end. The lower end of the cable 69 is similarly 14 loosely fitted through a J-lock fitting 72a and is retained with a button stop 73. The 1/8 turn J-lock 72a adapts to disengagably 16 connect the cable to a matching J-lock receiving fitting 72b on 17 a second closing plate 74. The cable is of a suitable length 18 that the track sections may articulate freely with a flexing of 19 the cable, yet is short enough to retract within the track when the sections are drawn together. A protuberance 75a ext~n~i ng 21 from the first closing plate 70 is adapted to fit into a matching 22 opening;75b in the second closing plate 74. The protuberance 23 engages the or~;n~ 75b until a bolting flange 75c contacts the 24 second closing plate 74 thereby aligning and stabilizing the sections together. Locking means 76 such as bolts are employed 26 to rigidly join the track sections 64, 65. The bottom section 63 1 is similarly joined to the middle section 64 to complete the 2 torque track 20 assembly.
3Referring to Figures 14 and 15, the torque track 20 is 4 secured to the derrick 6 with an upper and a lower connection means 77, 78. The upper connection means 77 comprises a cable 79 6 attaching the upper joint end of the top track section 65 to a 7 suitable cross-brace 80 at the crown of the derrick 6 with a 8 clamping means 81. The upper connection means 77 includes a 9 vertical adjusting means 77b, such as a turnbuckle, to provide limited vertical adjustment. The torque track 20 is suspended by 11 this upper connection means 77 which is capable of stabilizing 12 horizontal movement of the torque track and yet freely rotates 13 when subjected to torque loading. The lower connection means 78 14 comprises a torque arm 82a connected to and projecting laterally from the torque track 20. The torque arm 82a may be connected 16 using any of a plurality of bolting holes (not shown) formed 17 along the track, to adapt to variable geometry of different 18 derricks 6. A torque beam 82b is connected to the torque arm to 19 connect to suitable bracing 83 on the derrick 6 near its robust base where reactive drilling torques may safely be absorbed. The 21 torque track 20 is designed with sufficient torsional rigidity to 22 transmit the full reactive drilling torque to the rigid lower 23 connection means 78 and into the substructure of the drilling rig 24 1. The torque beam 82b is rigidly attached to the bracing 83 on the derrick 6 with a clamping means 84a which permits connections 26 to be made without need for welding or other structural .~,.
, ~
~.. . .
1 modifications to be made to the derrick 6. The torque arm is 2 similarly rigidly attached to the torque beam with a clamping 3 means 84b. The clamping means 84a, 84b permit adjustments to re-4 align the torque track 20 to the wellbore as required.
The mechanism that permits the torque track to absorb 6 the reactive loads as substantially torque and to prevent side 7 loading of the upper structure of the derrick is not immediately 8 apparent.
9 Referring to Figure 22, a free body force diagram of the top drive housing 21, pivoting frame 102, and torque bushing 11 59 is shown. The top drive housing 21 is depicted as imparting 12 a CW torque Tl to the drill string 5. The drill string resists 13 the rotation and results in a CCW couple Cl into the frame.
14 Assume for the moment, that the drill string is infinitely stiff.The frame acts as a moment arm which attempts to rotate around 16 the drill string. The moment arm will impose purely side loading 17 ga into the torque b~)sh;ng 59 and in turn into the torque track 18 20. An equal and opposite balancing load Sl then exists in the 19 moment arm. To prevent free rotation of the rigid frame around the track due to the balancing force gl, a reactive side load Rl 21 must exist on the drill string. Similarly, a reactive side load 22 R~ must exist at the track. Should the assumption of the stiff 23 drill string be true, high side loading of the torque track would24 result. High side loads could deflect the track significantly and impose loading to the top of the derrick which is contrary to 26 the objective.
~ 6~
1 Referring to Figure 23, the drill string is found to 2 be, not infinitely stiff, but is actually weak in side loading.
3 If Rl is then essentially zero, the moment arm rotates 4 essentially freely and deflects an amount dl, typically a couple of inches. The track is strong in side loading and deflects only 6 a very small amount d2 to balance the small load Rl.
7 The track must rotate with the moment arm or frame, 8 being rigidly fixed thereto. The track has significant torsional 9 rigidity and resists this rotation. This resistance manifests as a couple C2 and permits a small twist or rotation of the track.
11 The reactive side load R2 on the track ~im;n; shes as the drill 12 string deflects, the load being absorbed in the couple C2. The 13 side loading Sl has thus been substantially converted to a 14 reactive torque 10A~; ng C2 into the track.
Several factors contribute to the drill string 5 being 16 weak and permitting the conversion of side loads to torque 17 loading. The drill string is normally long in length, has a 18 relatively small mom nt of inertia and it extends down through a 19 large rig-floor opening into the wellbore which offers little support. The drill string 5 is connected at its upper end to the 21 top drive unit 13 which is connected to the travelling block 10.
22 The travelling block is hung from the crown with cables 9 which 23 are not normally capable of sust~;n;ng side loads.
' ~
1 Two extreme cases exist which interfere with the side-2 to-torque load conversion mechanism. When the top drive is 3 positioned near the rig floor 2, and particularly when slips are 4 engaged at the rotary table, the drill string 5 is stiffened and cannot deflect. The pivoting frame 102 acts as a moment arm and 6 transfers pure side loading to the torque track 20. This extreme 7 case is adequately compensated by the close proximity of the 8 strong torque arm 82a and torque beam 82b connection, absorbing 9 side loads without subjecting the upper part of the derrick to reactive loading. The second case occurs when the top drive is 11 positioned at the top of the derrick 6. Theoretically, one could 12 shorten the length of the cable 9 to zero, thus stiffening the 13 drill string. This situation is highly unlikely to occur and in 14 the worst case would result in reactive load sharing between the torque track 20 and the derrick 6.
16 Operations other than drilling place special load 17 conditions on the torque track 20. Lifting of heavy loads from 18 the V-door 101 can place unusual side loads on the torque track 19 20, deflecting it away from the derrick 6. Of particular concern is the rebound effect when the load is released, potentially 21 permitting the torque track to strike the structure of the 22 derrick, often located ;mme~ately adjacent the track. In the 23 worst case, if the torque bushing 59 is moving at that instant, 24 it can collide with the derrick 6, potentially damaging both the derrick and the bushing.
1 As shown in Figure 14, it is preferable to install a 2 steadying means such as turnbuckles 105, connected between the 3 derrick and torque track at vertically spaced points. Bars 106 4 having a plurality of connecting sites are attached to the torque track 20. Connection of the turnbuckle 105 to each bar 106 is 6 loose enough to permit reactive load movement but is sufficiently 7 rigid to prevent contact of the torque bushing 59 with the 8 derrick 6. Stated otherwise, the connection prevents the track 9 from moving toward or away from the back of the derrick but the connection is loose enough to allow the track to move sideways 11 and most importantly is loose enough that the connection cannot 12 transmit any torque.
13 Referring to Figures 16 and 17, at an elevation near 14 and below the lower end 38 of the saver sub 33, a backup wrench assembly 85 is provided comprising opposing rotation drill string 16 tongs 86 having stAn~rd oilfield tong jaw dies 87. Individual 17 hydraulic actuating means 88 are provided to cause the tong jaws 18 to hold the drill pipe 5 stationary while the drive shaft 22 is 19 appropriately rotated to connect or disconnect the saver sub joint 38, 39 thereto. The wrench assembly 85 makes it possible 21 to make or break the tool joint at any position in the derrick.
22 The wrench ~ssembly 85 is secured to the lower portion of the top 23 drive housing 21 with a spring mount means 89. When disengaging 24 a drill pipe 5 from the saver sub 33, the wrench assembly is positioned to engage the top of the pipe. As the saver sub is 26 screwed out of the drill pipe 5, the springs 89 deflect, ~ ~. ~.
, .
,, 1 permitting both the pipe 5 and the wrench assembly 85 to be moved 2 down by the pitch action of the threads.
3 A hydraulic cylinder 95 is pivotally connected at its 4 en~s by horizontal pin and hole means 203, 204 with the torque bushing 59 and top drive housing 21. Extension of the cylinder 6 90 will shift the top drive unit 13 forwardly; the pivoting frame 7 102 accommodates this movement. The top drive unit 13 can thus 8 be biased to an alternate position, such as over the mousehole 9 100.
It may not be feasible to locate the torque track 20 at the 11 back of the derrick 6. This can occur in the case of a portable 12 rig 103 having a le~n;ng derrick 6, where an obstacle free path 13 is not available from the rig floor 2 to the crown of the derrick 14 (Figures 20 and 21). In this case, the torque track 20 may be installed at right angles from the wellbore 3 and mousehole 100 16 alignment. The torque track 20 is suspended from the crown brace 17 80 with the upper connection means 77 as previously described, 18 but the lower connection means 78 is provided by a telescoping 19 torque beam assembly 96, whereby the first end of the beam 97 is secured to the robust base of the derrick 6 with the clamping 21 means 84 and the -s~con~ end 98 is moveable with respect to the 22 first and i8 pivotally connected to the torque track 20. An 23 exten~ing and retracting means 99 is provided to extend the 24 second end 98 with respect to the first end, resulting in a pivoting of the entire track 20, from the crown bracing 80, 26 thereby ext~n~ing the top drive unit 13 from a position over the l~ ~
21186~8 1 wellbore 3 to an alternate position such as over the mousehole 2 100.
3 With the ~extend" feature, several advantages in pipe 4 handling and efficiency are realized. The extend feature permits the mousehole, offset from the wellbore, to be drilled by the top 6 drive. It is possible to make up drill pipe connections at the 7 mousehole with the joint connection at the rig floor, at eye 8 level. Stands of drill pipe can be made up over the mousehole, 9 improving drilling efficiency. When drilling, the top drive may drill to the floor and, using a combination of extend and the 11 tilt elevator, one can simultaneously pick up a new length of 12 pipe from the V-door. The extend feature may also be used to 13 further assist the derrickman in handling drill collars, as the 14 bales and elevator can then bring the particularly heavy collars closer.
Claims (9)
1. A portable top drive assembly for use with a drilling rig having an upstanding derrick operatively aligned over a wellbore, said derrick supporting hoisting means, a swivel and a drill string extending into the wellbore, said top drive assembly comprising:
a top drive unit comprising a housing, a drive assembly supported by the housing, and a tubular drive shaft assembly extending vertically through the housing and being connected with the drive assembly for rotation thereby, said drive shaft assembly having upper and lower ends and being connected at its lower end with the drill string and at its upper end with the swivel for suspension from the derrick by the hoisting means;
the top drive unit being operative to develop reactive side and torque loads in the housing when the drive shaft rotates the drill string; and apparatus for transmitting the reactive loads from the housing to the rig comprising a linearly extending, substantially rigid torque track extending vertically in the derrick along the major part of the derrick's length, said track having upper and lower ends, said track being parallel with and laterally offset from the wellbore, said track being formed of sections joined end to end, means for disengagably and rigidly connecting the track sections end to end, means for rigidly connecting the track at its lower end with the rig so that reactive loads applied to the track are transmitted therethrough to the rig and so that the track is held upright in the derrick, the track otherwise being free of rigid connection with the derrick so that it can twist axially and deflect laterally relative to the derrick, a torque bushing rigidly engaging the track so that it can slide therealong but cannot rotate thereon, said bushing being operative to transmit reactive loads applied to it to the track, and linking means, connecting the housing and the bushing, for rigidly restraining the housing against rotation relative to the bushing and track and for transmitting reactive side and torque loads from the housing to the track.
a top drive unit comprising a housing, a drive assembly supported by the housing, and a tubular drive shaft assembly extending vertically through the housing and being connected with the drive assembly for rotation thereby, said drive shaft assembly having upper and lower ends and being connected at its lower end with the drill string and at its upper end with the swivel for suspension from the derrick by the hoisting means;
the top drive unit being operative to develop reactive side and torque loads in the housing when the drive shaft rotates the drill string; and apparatus for transmitting the reactive loads from the housing to the rig comprising a linearly extending, substantially rigid torque track extending vertically in the derrick along the major part of the derrick's length, said track having upper and lower ends, said track being parallel with and laterally offset from the wellbore, said track being formed of sections joined end to end, means for disengagably and rigidly connecting the track sections end to end, means for rigidly connecting the track at its lower end with the rig so that reactive loads applied to the track are transmitted therethrough to the rig and so that the track is held upright in the derrick, the track otherwise being free of rigid connection with the derrick so that it can twist axially and deflect laterally relative to the derrick, a torque bushing rigidly engaging the track so that it can slide therealong but cannot rotate thereon, said bushing being operative to transmit reactive loads applied to it to the track, and linking means, connecting the housing and the bushing, for rigidly restraining the housing against rotation relative to the bushing and track and for transmitting reactive side and torque loads from the housing to the track.
2. The top drive assembly as set forth in claim 1:
wherein the linking means is angularly disposed and pivotally connected at its ends with the housing and bushing so that said linking means can pivot about horizontal axes to enable the top drive unit to be displaced laterally; and comprising linearly extendable means for displacing the top drive unit laterally.
wherein the linking means is angularly disposed and pivotally connected at its ends with the housing and bushing so that said linking means can pivot about horizontal axes to enable the top drive unit to be displaced laterally; and comprising linearly extendable means for displacing the top drive unit laterally.
3. The top drive assembly as set forth in claim 2:
wherein the linearly extendable means comprises cylinder means mounted between and pivotally connected to each of the housing and the bushing for pivoting about horizontal axes.
wherein the linearly extendable means comprises cylinder means mounted between and pivotally connected to each of the housing and the bushing for pivoting about horizontal axes.
4. The top drive assembly as set forth in claims 1, 2 or 3 comprising:
twistable, flexible cable means suspending the upper end of the track from the upper end of the derrick.
twistable, flexible cable means suspending the upper end of the track from the upper end of the derrick.
5. In a drilling rig having an upstanding derrick operatively aligned over a wellbore, said derrick supporting hoisting means, a swivel suspended from the hoisting means and a drill string extending into the wellbore, the improvement comprising:
a top drive unit comprising a housing, a drive assembly supported by the housing, said drive assembly comprising hydraulic motors and a gear assembly connected therewith, and a tubular drive shaft assembly extending vertically in the housing and being operatively connected with the gear assembly for rotation thereby, said drive shaft assembly having upper and lower ends and being connected at its lower end with the drill string and at its upper end with the swivel for suspension in the derrick by the hoisting means;
the top drive unit being operative to develop reactive side and torque loads in the housing when the drive shaft rotates the drill string;
apparatus for transmitting the reactive loads from the housing to the rig comprising a linearly extending, substantially rigid torque track extending vertically in the derrick along the major part of the derrick's length, said track having upper and lower ends, said track being parallel with and laterally offset from the wellbore, said track being formed of sections joined end to end, means for disengagably and rigidly connecting the track sections end to end, means for rigidly connecting the track at its lower end with the rig so that reactive loads applied to the track are transmitted therethrough to the rig and so that the track is held upright in the derrick, the track otherwise being free of rigid connection with the derrick so that it can twist axially and deflect laterally relative to the derrick, a torque bushing rigidly engaging the track so that it can slide therealong but cannot rotate thereon, said bushing being operative to transmit reactive loads applied to it to the track, and linking means, connecting the housing and the bushing, for rigidly restraining the housing against rotation relative to the bushing and track and for transmitting reactive side and torque loads from the housing to the track;
a portable independent power supply unit for driving the hydraulic motors with hydraulic fluid; and a bundle of hoses, suspended from the derrick and operatively connecting the power supply unit and motors for conveying fluid therebetween.
a top drive unit comprising a housing, a drive assembly supported by the housing, said drive assembly comprising hydraulic motors and a gear assembly connected therewith, and a tubular drive shaft assembly extending vertically in the housing and being operatively connected with the gear assembly for rotation thereby, said drive shaft assembly having upper and lower ends and being connected at its lower end with the drill string and at its upper end with the swivel for suspension in the derrick by the hoisting means;
the top drive unit being operative to develop reactive side and torque loads in the housing when the drive shaft rotates the drill string;
apparatus for transmitting the reactive loads from the housing to the rig comprising a linearly extending, substantially rigid torque track extending vertically in the derrick along the major part of the derrick's length, said track having upper and lower ends, said track being parallel with and laterally offset from the wellbore, said track being formed of sections joined end to end, means for disengagably and rigidly connecting the track sections end to end, means for rigidly connecting the track at its lower end with the rig so that reactive loads applied to the track are transmitted therethrough to the rig and so that the track is held upright in the derrick, the track otherwise being free of rigid connection with the derrick so that it can twist axially and deflect laterally relative to the derrick, a torque bushing rigidly engaging the track so that it can slide therealong but cannot rotate thereon, said bushing being operative to transmit reactive loads applied to it to the track, and linking means, connecting the housing and the bushing, for rigidly restraining the housing against rotation relative to the bushing and track and for transmitting reactive side and torque loads from the housing to the track;
a portable independent power supply unit for driving the hydraulic motors with hydraulic fluid; and a bundle of hoses, suspended from the derrick and operatively connecting the power supply unit and motors for conveying fluid therebetween.
6. The improvement as set forth in claim 5 comprising:
a load collar carried by the drive shaft assembly;
a pair of bales pivotally suspended from the load collar;
an elevator carried by the bales; and linearly extendable means, pivotally connected with the housing and bales, for pivoting the bales upwardly a generally horizontal position.
a load collar carried by the drive shaft assembly;
a pair of bales pivotally suspended from the load collar;
an elevator carried by the bales; and linearly extendable means, pivotally connected with the housing and bales, for pivoting the bales upwardly a generally horizontal position.
7. The improvement as set forth in claim 5:
wherein the linking means is angularly disposed and pivotally connected at its ends with the housing and bushing so that said linking means can pivot about horizontal axes to enable the top drive unit to be displaced laterally; and comprising linearly extendable means for displacing the top drive unit laterally.
wherein the linking means is angularly disposed and pivotally connected at its ends with the housing and bushing so that said linking means can pivot about horizontal axes to enable the top drive unit to be displaced laterally; and comprising linearly extendable means for displacing the top drive unit laterally.
8. The improvement as set forth in claim 7:
wherein the linearly extendable means comprises cylinder means mounted between and pivotally connected to each of the housing and the bushing for rotation about horizontal axes.
wherein the linearly extendable means comprises cylinder means mounted between and pivotally connected to each of the housing and the bushing for rotation about horizontal axes.
9. The improvement as set forth in claims 5, 7 or 8 comprising:
twistable, flexible cable means suspending the upper end of the track from the upper end of the derrick.
twistable, flexible cable means suspending the upper end of the track from the upper end of the derrick.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US08/093,721 | 1993-07-20 | ||
| US08/093,721 US5433279A (en) | 1993-07-20 | 1993-07-20 | Portable top drive assembly |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CA2118608A1 CA2118608A1 (en) | 1995-01-21 |
| CA2118608C true CA2118608C (en) | 1996-03-19 |
Family
ID=22240373
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002118608A Expired - Lifetime CA2118608C (en) | 1993-07-20 | 1994-03-09 | Portable top drive assembly |
Country Status (2)
| Country | Link |
|---|---|
| US (1) | US5433279A (en) |
| CA (1) | CA2118608C (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101492996B (en) * | 2008-01-25 | 2011-05-25 | 中国石油天然气集团公司 | Method for controlling rotate speed torquemoment of top driving device of oil rig |
Families Citing this family (92)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5755296A (en) * | 1994-09-13 | 1998-05-26 | Nabors Industries, Inc. | Portable top drive |
| US5921329A (en) * | 1996-10-03 | 1999-07-13 | Sundowner Offshore Services, Inc. | Installation and removal of top drive units |
| US6536520B1 (en) | 2000-04-17 | 2003-03-25 | Weatherford/Lamb, Inc. | Top drive casing system |
| US6742596B2 (en) * | 2001-05-17 | 2004-06-01 | Weatherford/Lamb, Inc. | Apparatus and methods for tubular makeup interlock |
| US7140445B2 (en) * | 1997-09-02 | 2006-11-28 | Weatherford/Lamb, Inc. | Method and apparatus for drilling with casing |
| GB9815809D0 (en) * | 1998-07-22 | 1998-09-16 | Appleton Robert P | Casing running tool |
| GB2340859A (en) * | 1998-08-24 | 2000-03-01 | Weatherford Lamb | Method and apparatus for facilitating the connection of tubulars using a top drive |
| GB2340857A (en) | 1998-08-24 | 2000-03-01 | Weatherford Lamb | An apparatus for facilitating the connection of tubulars and alignment with a top drive |
| GB2340858A (en) * | 1998-08-24 | 2000-03-01 | Weatherford Lamb | Methods and apparatus for facilitating the connection of tubulars using a top drive |
| GB2345074A (en) | 1998-12-24 | 2000-06-28 | Weatherford Lamb | Floating joint to facilitate the connection of tubulars using a top drive |
| GB2347441B (en) | 1998-12-24 | 2003-03-05 | Weatherford Lamb | Apparatus and method for facilitating the connection of tubulars using a top drive |
| US7325610B2 (en) | 2000-04-17 | 2008-02-05 | Weatherford/Lamb, Inc. | Methods and apparatus for handling and drilling with tubulars or casing |
| GB2365463B (en) * | 2000-08-01 | 2005-02-16 | Renovus Ltd | Drilling method |
| CA2413825C (en) * | 2002-12-10 | 2007-07-17 | Allan R. Nelson Engineering (1997) Inc. | Telescoping rig with torque carrier |
| US6802378B2 (en) | 2002-12-19 | 2004-10-12 | Noble Engineering And Development, Ltd. | Method of and apparatus for directional drilling |
| USRE42877E1 (en) | 2003-02-07 | 2011-11-01 | Weatherford/Lamb, Inc. | Methods and apparatus for wellbore construction and completion |
| US7874352B2 (en) | 2003-03-05 | 2011-01-25 | Weatherford/Lamb, Inc. | Apparatus for gripping a tubular on a drilling rig |
| US7650944B1 (en) | 2003-07-11 | 2010-01-26 | Weatherford/Lamb, Inc. | Vessel for well intervention |
| CA2436296C (en) * | 2003-07-31 | 2007-05-15 | Estec Oilfield Inc. | Rig with torque carrier |
| EP1676015B1 (en) * | 2003-10-09 | 2010-02-10 | Varco I/P, Inc. | Make-up control system for tubulars |
| JP2007521424A (en) * | 2003-10-09 | 2007-08-02 | バーコ アイ／ピー，インコーポレイティド | Tubular makeup control system |
| US7377324B2 (en) * | 2003-11-10 | 2008-05-27 | Tesco Corporation | Pipe handling device, method and system |
| US7320374B2 (en) | 2004-06-07 | 2008-01-22 | Varco I/P, Inc. | Wellbore top drive systems |
| US7188686B2 (en) * | 2004-06-07 | 2007-03-13 | Varco I/P, Inc. | Top drive systems |
| CA2512570C (en) | 2004-07-20 | 2011-04-19 | Weatherford/Lamb, Inc. | Casing feeder |
| ATE495341T1 (en) * | 2004-11-08 | 2011-01-15 | Tesco Corp | TORQUE AMPLIFIER FOR HANDLING WELL TUBES |
| US7055594B1 (en) * | 2004-11-30 | 2006-06-06 | Varco I/P, Inc. | Pipe gripper and top drive systems |
| US7694744B2 (en) | 2005-01-12 | 2010-04-13 | Weatherford/Lamb, Inc. | One-position fill-up and circulating tool and method |
| CA2533115C (en) | 2005-01-18 | 2010-06-08 | Weatherford/Lamb, Inc. | Top drive torque booster |
| CA2633182C (en) * | 2005-12-12 | 2012-04-24 | Weatherford/Lamb, Inc. | Apparatus for gripping a tubular on a drilling rig |
| CA2578424C (en) * | 2006-02-08 | 2014-05-06 | Tesco Corporation | Method and assembly for casing handling using a kelly rig |
| GB2437647B (en) | 2006-04-27 | 2011-02-09 | Weatherford Lamb | Torque sub for use with top drive |
| US7487848B2 (en) * | 2006-04-28 | 2009-02-10 | Varco I/P, Inc. | Multi-seal for top drive shaft |
| US7401664B2 (en) * | 2006-04-28 | 2008-07-22 | Varco I/P | Top drive systems |
| US20080060818A1 (en) * | 2006-09-07 | 2008-03-13 | Joshua Kyle Bourgeois | Light-weight single joint manipulator arm |
| US7882902B2 (en) | 2006-11-17 | 2011-02-08 | Weatherford/Lamb, Inc. | Top drive interlock |
| US7472762B2 (en) * | 2006-12-06 | 2009-01-06 | Varco I/P, Inc. | Top drive oil flow path seals |
| US7665530B2 (en) | 2006-12-12 | 2010-02-23 | National Oilwell Varco L.P. | Tubular grippers and top drive systems |
| US20080230274A1 (en) | 2007-02-22 | 2008-09-25 | Svein Stubstad | Top drive washpipe system |
| US7748445B2 (en) | 2007-03-02 | 2010-07-06 | National Oilwell Varco, L.P. | Top drive with shaft seal isolation |
| US7784834B2 (en) * | 2007-03-28 | 2010-08-31 | Varco I/P, Inc. | Clamp apparatus for threadedly connected tubulars |
| US7784535B2 (en) * | 2007-06-27 | 2010-08-31 | Varco I/P, Inc. | Top drive systems with reverse bend bails |
| NO2957708T3 (en) * | 2007-12-12 | 2018-06-30 | ||
| US20090159271A1 (en) * | 2007-12-21 | 2009-06-25 | Bastiaan De Jong | Top drive systems for wellbore & drilling operations |
| US7637329B2 (en) * | 2008-01-17 | 2009-12-29 | National Oilwell Varco, L.P. | Methods and systems for drilling auxiliary holes |
| US8047303B2 (en) * | 2008-02-29 | 2011-11-01 | National Oilwell Varco L.P. | Drilling rig drawworks installation |
| US7854265B2 (en) * | 2008-06-30 | 2010-12-21 | Tesco Corporation | Pipe gripping assembly with power screw actuator and method of gripping pipe on a rig |
| GB0817307D0 (en) * | 2008-09-22 | 2008-10-29 | Churchill Drilling Tools Ltd | Apparatus for use in top filling of tubulars and associated methods |
| US7770668B2 (en) * | 2008-09-26 | 2010-08-10 | Longyear Tm, Inc. | Modular rotary drill head |
| CA2663348C (en) * | 2009-04-15 | 2015-09-29 | Shawn J. Nielsen | Method of protecting a top drive drilling assembly and a top drive drilling assembly modified in accordance with this method |
| US8191621B2 (en) * | 2009-05-29 | 2012-06-05 | Tesco Corporation | Casing stabbing guide and method of use thereof |
| US8424616B2 (en) | 2010-02-23 | 2013-04-23 | National Oilwell Varco, L.P. | Track guiding system |
| US20110280104A1 (en) * | 2010-03-05 | 2011-11-17 | Mcclung Iii Guy L | Dual top drive systems and methods for wellbore operations |
| US8181721B1 (en) * | 2010-08-23 | 2012-05-22 | Keast Larry G | Torque track and slide assembly |
| US8651175B2 (en) | 2011-01-14 | 2014-02-18 | Tesco Corporation | Top drive output torque measurement method |
| US8739888B2 (en) | 2011-04-28 | 2014-06-03 | Tesco Corporation | Mechanically actuated casing drive system tool |
| US9010410B2 (en) | 2011-11-08 | 2015-04-21 | Max Jerald Story | Top drive systems and methods |
| US9404318B2 (en) * | 2012-06-29 | 2016-08-02 | Tesco Corporation | Top drive counter moment system |
| EP2976496B1 (en) | 2013-03-20 | 2017-06-28 | Schlumberger Technology B.V. | Drilling system control |
| US10626683B2 (en) | 2015-08-11 | 2020-04-21 | Weatherford Technology Holdings, Llc | Tool identification |
| US10465457B2 (en) | 2015-08-11 | 2019-11-05 | Weatherford Technology Holdings, Llc | Tool detection and alignment for tool installation |
| EP4187056A1 (en) | 2015-08-20 | 2023-05-31 | Weatherford Technology Holdings, LLC | Top drive torque measurement device |
| US10323484B2 (en) | 2015-09-04 | 2019-06-18 | Weatherford Technology Holdings, Llc | Combined multi-coupler for a top drive and a method for using the same for constructing a wellbore |
| CA2997615A1 (en) | 2015-09-08 | 2017-03-16 | Weatherford Technology Holdings, Llc | Genset for top drive unit |
| US10590744B2 (en) | 2015-09-10 | 2020-03-17 | Weatherford Technology Holdings, Llc | Modular connection system for top drive |
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| US10745978B2 (en) | 2017-08-07 | 2020-08-18 | Weatherford Technology Holdings, Llc | Downhole tool coupling system |
| US11047175B2 (en) | 2017-09-29 | 2021-06-29 | Weatherford Technology Holdings, Llc | Combined multi-coupler with rotating locking method for top drive |
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| US10782197B2 (en) | 2017-12-19 | 2020-09-22 | Schlumberger Technology Corporation | Method for measuring surface torque oscillation performance index |
| US10760417B2 (en) | 2018-01-30 | 2020-09-01 | Schlumberger Technology Corporation | System and method for surface management of drill-string rotation for whirl reduction |
| CN108194031A (en) * | 2018-02-26 | 2018-06-22 | 四川宏华石油设备有限公司 | A kind of top drive guide rail |
| US10895111B1 (en) * | 2019-07-10 | 2021-01-19 | Gordon Bros. Supply, Inc. | Guide for top drive unit |
-
1993
- 1993-07-20 US US08/093,721 patent/US5433279A/en not_active Expired - Lifetime
-
1994
- 1994-03-09 CA CA002118608A patent/CA2118608C/en not_active Expired - Lifetime
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101492996B (en) * | 2008-01-25 | 2011-05-25 | 中国石油天然气集团公司 | Method for controlling rotate speed torquemoment of top driving device of oil rig |
Also Published As
| Publication number | Publication date |
|---|---|
| CA2118608A1 (en) | 1995-01-21 |
| US5433279A (en) | 1995-07-18 |
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