Note: Descriptions are shown in the official language in which they were submitted.
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TOP DRIVE
This is a divisional application of copending
Canadian Application Serial No.: 2,563,938 filed June 7,
2005.
The present invention relates to a top drive,
particularly but not exclusively, to a top drive for use
in drilling, construction, repair and maintenance of an
oil or gas well. The present invention also relates to
various components in or for use with a top drive.
The prior art discloses a variety of apparatuses
which use a DC or AC motor. U.S. Patents 4,458,768;
5,433,279; 6,276,450; 4,813,493; 6,705,405; 4,800,968;
4,878,546; 4,872,577; 4,753,300; 6,536,520; 6,679,333
disclose various apparatuses.
The prior art discloses a Varco Drilling Systems TDS-
9S AC Top DriveTM with an alternating current motor-
powdered top drive.
In accordance with a first aspect of the present
invention, there is provided an apparatus for use in a top
drive for releasably holding a tubular, the apparatus
comprising at least two opposed clamping apparatuses,
spaced-apart for selective receipt of a tubular to be
clamped therebetween, each of the two opposed clamping
apparatuses having a mount and a piston movable within the
mount, the piston selectively movable toward and away from
a tubular to be clamped, two spaced-apart telescopic legs
which in use depend from a part of the top drive, the
telescopic legs for moving the at least two opposed
clamping apparatus in a substantially vertical plane.
Preferably, the tubular comprises one of: pipe, casing,
tubing, saver sub, and quill of an apparatus.
Preferably, the two opposed clamping apparatuses
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comprises a spring.
A second aspect of the present invention provides
apparatus for use in a top drive for releasably holding a
tubular, the apparatus comprising at least two opposed
clamping apparatuses, spaced-apart for selective receipt
of a tubular to be clamped therebetweeen, each of the
two opposed clamping apparatuses having a mount and a
piston movable within the mount, the piston selectively
movable toward and away from a tubular to be clamped,
two spaced-apart telescopic legs which in use depend
from a part of the top drive, the telescopic legs for
moving the at least two opposed clamping apparatus in a
substantially vertical plane. Preferably, the tubular
comprises one of: pipe, casing, tubing, saver sub, and
quill of a apparatus.
Preferably, the two opposed clamping apparatuses
are releasably connected together with connection
apparatus so that either or both connection apparatuses
are disconnectible. Preferably, the two halves openable
to receive a tubular to be clamped upon disconnection of
one of the two connection apparatuses, the two halves
separable and movable apart upon disconnection of both
connection apparatuses. Advantageously, each connection
apparatus comprises a plurality of spaced-apart
intermeshing lugs with holes therein and a pin removably
insertable through the holes. Preferably, such that a
hinge is formed. Advantageously, the two telescopic legs
have a non-circular cross-section. Preferably,
rectangular, oblong or square in cross-section.
Preferably, the apparatus further comprises a spring
apparatus within each telescopic leg for compensating for
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movement of a tubular clamped by the apparatus.
Preferably, the compensation facilitates stabbing, in
that damage is less likely to occur in mating threads
when at least the majority of the weight of the tubular
to be connected to a string is compensated for.
Advantageously, the apparatus further comprises a piston
and cylinder in each telescopic leg, the cylinder with
a vacuum therein and as a piston extensible from and
retractable within the hollow cylinder, the piston and
providing compensation for movement of the member clamped
by the clamping apparatus.
Preferably, the telescopic legs each comprise an
outer leg portion and an inner leg portion further
comprising a chain connection structure on each outer leg
portion and each inner leg portion to which a chain is
connectible to prevent separation of the outer leg
portion from the inner leg portion. Advantageously, the
apparatus further comprises guide apparatus secured to
and below the two opposed clamping apparatuses for
guiding a tubular between the two opposed clamping
apparatuses. Preferably, the guide apparatus is
releasably connected to at least one of the two opposed
clamping apparatuses. Preferably, chained or pinned.
Advantageously, the apparatus further comprises
generator apparatus connected to one of the two legs for
generating electrical power. Preferably, the apparatus
further comprises electrical distribution apparatus.
Advantageously, the generator apparatus converts
hydraulic power from fluid flow and/or pressure into
electricity. Thus providing a top drive with an
electrical power generator which is rotatable with pipe
handling apparatus
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Preferably, the further comprises a hydraulic fluid
manifold connected to at least one of the two telescopic
legs for receiving hydraulic fluid from an hydraulic
fluid source and for providing hydraulic fluid for
releasably clamping and holding a member for wellbore
operations. Preferably, for supplying hydraulic fluid to
another item below the apparatus. Advantageously, the
hydraulic fluid manifold includes a plurality of
hydraulic fluid conduits and a plurality of controllable
valves for selectively controlling fluid flow in each
hydraulic fluid conduit. Preferably, the apparatus
further comprises generator apparatus connected to at
least one of the two legs for generating electrical
power, and controller apparatus on one of the two legs in
communication with the controllable valves for
controlling the controllable valves.
Preferably, controller apparatus includes digital
signal processing apparatus and an antenna for
communicating with the controller apparatus from a
location spaced-apart from the apparatus for releasably
clamping and holding a tubular for wellbore operations.
Advantageously, each piston comprises a die holder
and die apparatus for engaging the tubular member.
Preferably, each housing has a cylinder lining the
housing, the piston slideably arranged in the cylinder.
Preferably, the apparatus further comprises a
connection structure on each of the two telescopic legs
for connecting the apparatus to the top drive.
Preferably, to a rotation apparatus for rotation thereby.
Advantageously, the connection structure provides a
pivotable connection of each telescopic leg at its upper
end for pivoting the two telescopic legs apart from each
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other.
Preferably, the two legs further comprise an anti-
rotation structure for receiving part of an adjacent
apparatus and releasably holding the part so that the
adjacent apparatus is rotatable simultaneously with the
apparatus for releasably clamping and holding a member
for wellbore operations.
The second aspect of the invention also provides a
top drive comprising a drive motor and an apparatus of
the invention.
The second aspect of the invention also provides a
method for gripping an item, the method comprising the
steps of positioning the item within a main body of an
apparatus, the apparatus comprising a main body, two
opposed clamping apparatuses in the main body, the two
opposed clamping apparatuses spaced-apart for selective
receipt therebetween of a member to be clamped
therebetweeen, each of the two opposed clamping
apparatuses having a mount and piston apparatus movable
within the mount, the piston apparatus selectively
movable toward and away from a member to be clamped, two
legs, the legs spaced-apart and each leg with an upper
end and a lower end, each lower end connected to the main
body, each leg comprising an outer leg portion and an
inner leg portion, the inner leg portion having part
thereof movable within the outer leg portion to provide a
range of up/down movement for the main body, wherein the
member for wellbore operations is a tubular member, and
each piston apparatus including a piston and a die holder
secured to an outer end of the piston, and die apparatus
on the die holder for engaging the tubular member, each
mount having a liner removably disposed therein, each
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piston movable within a corresponding liner, and moving
the pistons so that the die apparatus engages the item to
be gripped thereby gripping the item.
Preferably, the method further comprises the step of
rotating the apparatus thereby rotating the item gripped
by the apparatus.
A third aspect of the present invention provides a
top drive comprising a drive motor, and a support
apparatus and tubular handling apparatus connected to and
below and supported by the support apparatus, the
tubular handling apparatus including hydraulic-fluid-
powered apparatus on or below the tubular handling
apparatus, provision apparatus connected to the tubular
handling apparatus for providing hydraulic fluid to power
the hydraulic-fluid-powered apparatus, the provision
apparatus including flow line apparatus for providing
hydraulic fluid to the hydraulic-fluid-powered apparatus
and electrically-operable control apparatus for
controlling fluid flow to and from the flow line
apparatus, and electrical power generating apparatus
connected to the tubular handling apparatus for providing
electrical power to the electrically-operable control
apparatus.
Preferably, the top drive further comprises a gear
apparatus, a drive quill coupled to the gear apparatus
and a suspension arrangement. Preferably, the tubular
handling apparatus includes clamping apparatus for
clamping an item, the clamping apparatus powered by
hydraulic fluid from the provision apparatus.
Advantageously, the clamping apparatus is rotatable with
respect to the drive motor, the support apparatus
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including a locking mechanism for selectively locking the
tubular handling apparatus in position, the locking
mechanism comprising driving apparatus for rotating the
clamping apparatus, the drive quill rotatable by the gear
apparatus with the clamping apparatus locked in position
by the locking mechanism.
Preferably, the electrically-operable control
apparatus includes a plurality of selectively operable
control valves which selectively control flow of
hydraulic fluid to apparatuses below the support
apparatus. Advantageously, the apparatuses below the
lower support apparatus include clamping apparatus for
clamping an item, elevator for supporting an item, and
link-tilt apparatus for moving the elevator at an angle
to the support apparatus. Preferably, the clamping
appapratus comprises at least two opposed clamping
apparatuses, spaced-apart for selective receipt of a
tubular to be clamped therebetweeen, each of the two
opposed clamping apparatuses having a mount and a piston
movable within the mount, the piston selectively
movable toward and away from a tubular to be clamped,
two spaced-apart telescopic legs which in use depend
from a part of the top drive, the telescopic legs for
moving the at least two opposed clamping apparatus in a
substantially vertical plane.
Preferably, the top drive further comprises a piston
and cylinder in each telescopic leg with a first part
thereof connected to the upper end and a second part
thereof connected to the lower end, each piston and
cylinder wherein the cylinder has a vacuum therein and
the piston is extensible from and retractable within the
cylinder, the piston and cylinder providing compensation
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for movement of the tubular clamped by the clamping
apparatus, fluid to power the piston and cylinder
provided by the provision apparatus.
Advantageously, the generator apparatus for
generating electrical power is connected to one of the
two telescopic legs. Preferably, the provision apparatus
comprises a hydraulic fluid manifold connected to one of
the two telescopic legs for receiving hydraulic fluid
from an hydraulic fluid source and for providing
hydraulic fluid to the generator apparatus to power the
generator apparatus. Advantageously, the hydraulic fluid
manifold includes a plurality of hydraulic fluid conduits
and a plurality of controllable valves for selectively
controlling fluid flow in each hydraulic fluid conduit.
Preferably, the top drive further comprises a rotating
head connected to and between the two telescopic legs,
the rotating head for receiving hydraulic fluid from a
fluid supply and for providing the hydraulic fluid to
power the generator. Advantageously, the rotating head
provides hydraulic fluid for the plurality of
controllable valves.
Preferably, the drive motor is an alternating
current permanent magnet motor having a bore
therethrough, a planetary gear apparatus coupled to the
alternating current permanent magnet motor, the planetary
gear apparatus having a bore therethrough, the bore
through the alternating current permanent magnet motor
substantially aligned with the bore through the planetary
gear apparatus so that fluid is flowable therethrough,
the top drive further comprising a quill drivingly
connected to the planetary gear apparatus to rotate the
quill.
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Preferably, the suspension arrangement comprises a
swivel body, a suspension member above the permanent
magnet motor, at least one link arranged between the
swivel body and the suspension member. Preferably, the
swivel body is located below the planetary gear
apparatus. Advantageously, two links are arranged between
the swivel body and the suspension member. Preferably,
the at least one link is provided with an opening
therethrough for receiving a pin or ear, the opening
oversized to allow a degree of vertical movement.
Preferably a non-circular opening, most preferably
elongate. Advantageously, the suspension member comprises
a block having sheaves and a becket rigidly fixed
thereto, the sheaves connectable to a rope to a derrick
of a rig and the becket connected to the at least one
link. Preferably, rotatably fixed thereto and
advantageously, releasably fixed thereto. Advantageously,
the becket is selectively securable to the travelling
block in a plurality of positions. Preferably, the top
drive further comprises a weight compensation device
arranged between the becket and the swivel body for
compensating for the weight of the top drive and a
tubular to be stabbed during a stabbing operation to
inhibit damage to tubulars. Preferably, the weight
compensation device comprises a hydraulic piston and
cylinder and an accumulator. Advantageously, the swivel
body has an interior, a main bearing disposed within the
interior, the quill having a flange resting on and
rotatable on the main bearing. Preferably, the top drive
further comprises a load sleeve retained by the swivel
body, the quill rotatable within the load sleeve, a load
collar positioned around the load sleeve and supported
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thereby, at least one bail depending from the load collar
and an elevator for selectively receiving and holding a
tubular, the elevator supported by the at least one
bail.
Preferably, the top drive further comprises an
access platform pivotably connected at a lower end to the
swivel body, the access platform with a platform portion
pivotable to a generally horizontal position so that
personnel on the access platform can access components of
the top drive.
Advantageously, the top drive further comprises an
extension mechanism for moving the top drive
horizontally. Preferably the extension mechanism
comprises a plurality of piston and cylinders and a
frame. Preferably, the extension mechanism has an opening
through which a tubular stand is movable while the
extension mechanism with the top drive connected thereto
moves with respect to the tubular stand.
A fourth aspect of the present invention provides a
containerized apparatus comprising a container, top drive
removably disposed within the container, an extension
mechanism for moving the top drive generally horizontally
within a derrick, the top drive secured to the extension
mechanism, the extension mechanism removably disposed
within the container with the top drive, a track for
the top drive to move in a vertical plane in use in a
derrick, the track comprised of multiple track parts
connectible together, a skid for retaining the top drive
during transit, a part of the skid forming at least one
track part. Alternatively or preferably, the skid forms a
torque frame, such that the skid forms part of the top
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drive in use to help react the torque of the drive motor.
Preferably, the container is an ISO container, preferably
a 40'x8'x8,5' ISO container.
Preferably, the track further comprises at least one
first compartment for removably storing the multiple
track parts, the multiple track parts removably located
in the at least one first compartment, and the multiple
track parts assembleable outside the container to include
the multiple track parts and the at least one skid track
part with the extension mechanism movable along the track
with the top drive. Advantageously, the multiple track
parts include at least one length-adjustable track part
so that the track is installable in derricks of different
height. Preferably, the top drive apparatus includes a
motor, a gear system, and tubular handling apparatus, the
tubular handling apparatus including an elevator for
selective holding a tubular and links to connect the
elevator to the top drive apparatus, the motor, gear
system and tubular handling apparatus removably disposed
within the container.
Preferably, the skid track part has fork lift
pockets for receiving fork lift projections.
Advantageously, at least one of the multiple track parts
has fork lift pockets for receiving fork lift
projections. Preferably, all of the multiple track parts
have fork lift pockets for receiving fork lift
projections.
Advantageously, the top drive includes an access
platform pivotably connected to a part of the top drive,
the access platform having a top end releasably connected
to the top drive, upon release of the top end of the
access platform the access platform pivotable from a
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position generally aligned with the apparatus to a
position generally normal thereto so that the access
platform provides a platform on which a person can stand
to access part of the apparatus, the access platform
removably located within the container with the
apparatus.
Preferably, the containerized apparatus further
comprises a suspension apparatus removably located within
the container, the suspension apparatus connected to the
top drive, the suspension apparatus for suspending the
top drive apparatus in a derrick. Preferably, the
suspension apparatus includes a travelling block, a hook
connectable to the travelling block, and a becket
connectable to the top drive apparatus and to the hook.
Advantageously, the suspension apparatus includes a block
and a becket, the becket directly connected to the block.
Preferably, the becket is selectively rotatable with
respect to the block and is securable to the block in a
chosen non-rotating position.
Advantageously, the track is connectible to a
derrick and is suitable for reacting torque generated by
the top drive apparatus to the derrick.
Preferably, the containerized apparatus further
comprises a control system in the container operable by
personnel in the container to control the apparatus when
the apparatus is removed from the container and located
in a derrick for operation.
Preferably, the containerized apparatus a further
comprises a power system within the container for
providing power to operate at least part of the top
drive. Preferably, the power system provides hydraulic
power.
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Advantageously, the containerized apparatus further
comprises a reservoir within the container holding
hydraulic fluid used by the power system for providing
hydraulic power to the apparatus. Preferably, the
containerized apparatus further comprises a cooling
system within the container for providing cooling to the
apparatus.
Preferably, the containerised apparatus has an
alternating current permanent magnet motor having a bore
therethrough, a planetary gear apparatus coupled to the
alternating current permanent magnet motor, the planetary
gear apparatus having a bore therethrough, the bore
through the alternating current permanent magnet motor
substantially aligned with the bore through the planetary
gear apparatus so that fluid is flowable therethrough,
the top drive further comprising a quill drivingly
connected to the planetary gear apparatus to rotate the
quill.
Advantageosuly, wherein the extension mechanism has
an opening through which a tubular stand is movable while
the extension mechanism with the top drive connected
thereto moves with respect to the tubular stand.
A fifth aspect of the present invention provides an
apparatus for wellbore operations, the apparatus
comprising a derrick, a guide beam connected to the
derrick, a top drive movable on the guide beam, a torque
reaction structure connected to the guide beam, and skid
apparatus held by the torque reaction structure, the skid
apparatus movable vertically with respect to the torque
reaction structure to inhibit a vertical load from
passing from the skid apparatus to the torque reaction
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structure.
Preferably, the derrick comprises a rig floor, the
guide beam has a topmost part, the topmost part
comprising an outer part and an inner part movable within
the outer part, and the inner part and outer part
selectively connectible at a plurality of different
locations to provide length adjustability to the guide
beam so that position of the guide beam with respect to
the rig floor is adjustable. Advantageously, the
apparatus further comprises a first shackle connected to
the derrick, a second shackle connected to the first
shackle and to the inner part of the topmost part of the
guide beam to inhibit torque transfer between the topmost
part and the derrick. Preferably, the apparatus further
comprises at least one secondary shackle connected to the
outer part of the topmost part for providing an
attachment for a cable, the cable connectible to the
derrick.
Advantageously, the wellbore operations are done at
a well, the well having a well centre, and wherein the
torque reaction structure includes a frame movable with
respect to the guide beam toward and away from the well
centre.
Preferably, the top drive comprises a load collar,
an elevator, two bails each with upper ends connected
to the load collar and lower ends connected to the
elevator, each bail comprising an outer body with an end
eye and an inner body with an end eye, the inner body
movable within the outer body to adjust length of the
bail, and the inner body selectively connectible to the
outer body at a plurality of locations to provide length
adjustability of the bails. Advantageously, the top drive
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comprises a gear apparatus and a gear collar wherein the
gear collar and the load collar are a single integral
piece.
Preferably, the top drive includes a top drive motor
and a quill, and a brake apparatus for braking the quill,
the brake apparatus having a brake hub about the quill,
the apparatus further comprising seal apparatus within
the brake hub for sealing a quill/brake hub interface,
the seal apparatus comprising a body with a first part
and a second part, the first part rotatable with the
quill, the second part with the top drive motor, and an
absorbent seal member between the first part of the seal
apparatus and the second part of the seal apparatus, the
absorbent seal member located so that force on it during
rotation forces lubricating fluid out of the absorbent
seal member, the absorbent seal member sealing an
interface between the first part and the second part.
Advantageously, the top drive has a drive motor and
includes a gear apparatus with a sun gear, the gear
apparatus located beneath the drive motor, the apparatus
further comprising a seal apparatus for selectively
engaging the sun gear to seal off a pathway from the gear
apparatus to the drive motor. Preferably, the seal
apparatus including a seal, a seal support supporting the
seal movably disposed within or on a body such that the
seal engages the sun gear to seal off the pathway, the
seal support movable by fluid under pressure applied to
the seal support, and resilient apparatus urging the
seal support so that the seal contacts the sun gear to
seal off the pathway when insufficient or no fluid under
pressure is applied to the seal support. Advantageously,
the resilient apparatus comprises a spring.
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Preferably, the top drive comprises an alternating
current permanent magnet motor having a bore
therethrough, a planetary gear apparatus coupled to the
alternating current permanent magnet motor, the planetary
gear apparatus having a bore therethrough, the bore
through the alternating current permanent magnet motor
substantially aligned with the bore through the planetary
gear apparatus so that fluid is flowable therethrough,
the top drive further comprising a quill drivingly
connected to the planetary gear apparatus to rotate the
quill.
Advantageously, the top drive comprises a suspension
arrangement having a swivel body, a suspension member
above the permanent magnet motor, at least one link
arranged between the swivel body and the suspension
member. Preferably, the top drive further comprises a
load sleeve retained by the swivel body, the quill
rotatable within the load sleeve, a load collar
positioned around the load sleeve and supported thereby,
at least one bail depending from the load collar and an
elevator for selectively receiving and holding a tubular,
the elevator supported by the at least one bail.
Preferably, the top drive further comprises an
access platform pivotably connected at a lower end to the
swivel body, the access platform with a platform portion
pivotable to a generally horizontal position so that
personnel on the access platform can access components of
the top drive.
Preferably, the apparatus further comprises an
extension mechanism for moving the top drive
horizontally. Preferably the extension mechanism
comprises a plurality of piston and cylinders and a
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frame. Advantageously, the extension mechanism has an
opening through which a tubular stand is movable while
the extension mechanism with the top drive connected
thereto moves with respect to the tubular stand.
A sixth aspect of the present invention provides an
apparatus for wellbore operations, the apparatus
comprising a guide beam connectible to a derrick with a
rig floor, the guide beam including a topmost part, the
topmost part comprising an outer part and an inner part
movable within the outer part, and the inner part and
outer part selectively connectible at a plurality of
different locations to provide length adjustability to
the guide beam so that position of the guide beam with
respect to the rig floor is adjustable.
Preferably, the apparatus further comprises a first
shackle connected to the derrick, a second shackle
connected to the first shackle and to the inner part of
the topmost part of the guide beam to inhibit torque
transfer between the topmost part and the derrick.
Advantageously, the apparatus further comprises at
least one secondary shackle connected to the outer part
of the topmost part for providing an attachment for a
cable, the cable connectible to the derrick.
A seventh aspect of the present invention provides
an apparatus for wellbore operations, the apparatus
comprising a derrick, a top drive movably connected to
the derrick, a connector below the top drive, elevator,
two bails each with upper ends connected to the connector
and lower ends connected to the elevator, each bail
comprising an outer body with an end eye and an inner
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body with an end eye, the inner body movable within the
outer body to adjust length of the bail, and the inner
body selectively connectible to the outer body at a
plurality of locations to provide length adjustability of
the bails.
An eighth aspect of the present invention provides a
top drive comprising drive motor and a quill, and a brake
apparatus for braking the quill, the brake apparatus
having a brake hub about the quill, the apparatus further
comprising seal apparatus within the brake hub for
sealing a quill/brake hub interface, the seal apparatus
comprising a body with a first part and a second part,
the first part rotatable with the quill, the second part
with the top drive motor, and an absorbent seal member
between the first part of the seal apparatus and the
second part of the seal apparatus, the absorbent seal
member located so that force on it during rotation forces
lubricating fluid out of the absorbent seal member, the
absorbent seal member sealing an interface between the
first part and the second part.
* * *
European Patent Publication Number 1 753 932 from
which this case is divided, claims a top drive for
wellbore operations, the top drive comprising an
alternating current permanent magnet motor having a bore
therethrough, a planetary gear apparatus coupled to the
alternating current permanent magnet motor, the planetary
gear apparatus having a bore therethrough, the bore
through the alternating current permanent magnet motor
substantially aligned with the bore through the planetary
gear apparatus so that fluid is flowable therethrough,
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the top drive further comprising a quill drivingly
connected to the planetary gear apparatus to rotate the
quill.
Preferably, the alternating current permanent magnet
motor is arranged above the planetary gear apparatus.
Preferably, directly on top of, perhaps spaced by a
spacer and/or means for inhibiting ingress of oil and
lubricants. Advantageously, the top drive further
comprises a support arrangement for supporting the
alternating current permanent magnet motor and the
planetary gear apparatus, the support arrangement
comprising a swivel body, a suspension member above the
permanent magnet motor, at least one link arranged
between the swivel body and the suspension member.
Preferably, the swivel body is located below the
planetary gear apparatus. Advantageously, two links are
arranged between the swivel body and the suspension
member. Preferably, the at least one link is provided
with an opening therethrough for receiving a pin or ear,
the opening oversized to allow a degree of vertical
movement. Preferably a non-circular opening, most
preferably elongate.
Advantageously, the suspension member comprises a
block having sheaves and a becket rigidly fixed thereto,
the sheaves connectable to a rope to a derrick of a rig
and the becket connected to the at least one link.
Preferably, rotatably fixed thereto and advantageously
fixable a various angles and advantageously, releasably
fixed thereto. Preferably, the becket is selectively
securable to the travelling block in a plurality of
positions.
Advantageously, the top drive further comprises a
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weight compensation device arranged between the becket
and the swivel body for compensating for the weight of
the top drive and a tubular to be stabbed during a
stabbing operation to inhibit damage to tubulars.
Preferably, the weight compensation device comprises a
hydraulic piston and cylinder and an accumulator.
Preferably, the swivel body has an interior, a main
bearing disposed within the interior, the quill having a
flange resting on and rotatable on the main bearing.
Advantageously, the top drive further comprises a load
sleeve retained by the swivel body, the quill rotatable
within the load sleeve, a load collar positioned around
the load sleeve and supported thereby, at least one bail
depending from the load collar and an elevator for
selectively receiving and holding a tubular, the elevator
supported by the at least one bail. Preferably, two bails
depend from the load collar from ears and support the
elevator on opposing sides of the elevator. Preferably,
the top drive further comprises a tilt apparatus for
tilting the at least one bail, the tilt apparatus
arranged to rotate the bails about the load collar for
tilting the at least one bail central line extending down
through a centre of the permanent magnet through a centre
of the planetary gear apparatus, through a centre of the
quill, the centres aligned. Advantageously, the tilt
apparatus comprises a clamp on the at least one bail,the
clamp having two roller pins between which a portion of
the at least one bail movable to facilitate movement of
the bail with respect to the clamps.
Preferably, the two roller pins are mounted with
mounting plates having offset holes for mounting the
roller pins so that reversing the mounting plates changes
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the distance between the roller pins to accommodate a
bail of different widths.
Advantageously, the top drive further comprises a
clamping apparatus rotatably arranged on the top drive,
the clamping apparatus for selectively clamping a
tubular.
Preferably, the load collar is freely rotatably
disposed, the clamping apparatus disposed between the two
bails, such that the load collar, bails and elevator can
rotate with the clamping mechanism. Advantageously, the
clamping apparatus comprises at least one two jaw for
selective receipt therebetween of a tubular to be clamped
therebetweeen. Preferably at least two jaws. The tubular
to be gripped or clamped in the clamping apparatus may be
a saver sub, a pipe, casing or a tool. Advantageously,
the at least one jaw comprises a piston movable within a
cylinder toward and away from a tubular to be clamped.
Preferably, the clamping apparatus further comprises at
least one telescopic leg. Preferably, the at least one
leg depends from the load collar. Advantageously, the
clamping apparatus comprises at least two spaced-apart
telescopic legs. Preferably, the top drive further
comprises at least one further motor.
Preferably, the top drive further comprises
electrical power generating apparatus connected to the
clamping apparatus for providing electrical power.
Advantageously, the top drive further comprises a
hydraulic manifold, a plurality of directional control
valves for control hydraulic fluid flow in a plurality of
corresponding flow lines, the plurality of corresponding
flow lines including flow lines for providing hydraulic
fluid to power apparatus below the clamping system.
CA 02634533 2008-07-08
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Preferably, the hydraulic manifold and the plurality of
directional control valves are arranged on the at least
one telescopic leg.
Preferably, the load sleeve has fluid conducting
channels and the apparatus further comprises a rotating
head connected to the load sleeve for receiving fluid
from the load sleeve's fluid conducting channels and for
conveying the fluid to the lower hydraulic manifold, and
the rotating head rotatable with the clamping apparatus.
Advantageously, the top drive further comprises a
selective locking mechanism secured to the swivel body
for selectively locking the clamping apparatus
preventing its rotation while the quill is allowed to
rotate. Preferably, the clamping apparatus depends from a
gear collar, which is movable or brakeable in response to
the locking mechanism. Most preferably, the clamping
apparatus is in rotational communication with the gear
collar and the load collar. The load collar and gear
collar may be integral and may be cast in a single unit.
Preferably, the top drive further comprises a mud saver
apparatus releasably connected to the quill. Preferably,
the top drive further comprises a saver sub. Preferably,
releasably connected to and below the mud saver
apparatus. Advantageously connected with a non-rotating
connecting means. Preferably, first connection locking
apparatus locks the quill to the mud saver apparatus, and
second connection locking apparatus locks the mud saver
apparatus to the saver sub.
Advantageously, a spacer plate is arranged between
the alternating current permanent magnet motor and the
planetary gear apparatus, the spacer plate having a
bearing recess, and a bearing in the bearing recess for
CA 02634533 2008-07-08
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facilitating rotation of the quill.
Preferably, the top drive further comprises an
access platform pivotably connected at a lower end to the
swivel body, the access platform with a platform portion
pivotable to a generally horizontal position so that
personnel on the access platform can access components of
the top drive.
Advantageously, the top drive further comprises an
extension mechanism for moving the top drive
horizontally. Preferably the extension mechanism
comprises a plurality of piston and cylinders and a
frame. Preferably, the extension mechanism has an opening
through which a tubular stand is movable while the
extension mechanism with the top drive connected thereto
moves with respect to the tubular stand.
CA 02634533 2008-07-08
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For a better understanding of the present invention,
reference will now be made, by way of example, to the
accompanying drawings, in which:
Figure 1A is a perspective view of an apparatus in
accordance with the present invention, the apparatus
comprising a top drive having a motor, a gearbox, a brake
system, a quill and a bonnet, the top drive slidably
arranged on a torque track, a becket and links connected
to a swivel body for suspending the top drive, an
elevator depending from a load collar on mechanically
movable bails, a clamping apparatus for clamping
tubulars, a gear collar, a locking mechanism and
connection lock member for selectively rotating the
clamping mechanism to facilitate the spinning and
torquing of connections between tubulars in a string, an
extension mechanism for moving the top drive in relation
to the torque track, a brake system for slowing and
halting rotation of the quill, and a mud saver apparatus,
a cross over sub and a saver sub;
Figure 1B is an exploded view of the apparatus shown
in Figure IA;
Figure 1C is a front view in cross-section of the
apparatus shown in Figure 1A, not showing the torque tube
or the clamping apparatus;
Figure 1D is a side view of the apparatus shown in
Figure 1A, not showing the torque tube;
Figure 1E is a top view of the apparatus shown in
Figure 1A;
Figure 1F is a front view of part of the apparatus
shown in Figure 1A;
Figure 1G is a side view of the quill of the top
drive shown in Figure 1A;
CA 02634533 2008-07-08
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Figure 1H is a perspective view of the quill shown
in Figure 1G;
Figure 1I is a cross-sectional view of an end of the
quill shown in Figure 1G;
Figures 1J and 1K are perspective views of the load
sleeve of the top drive shown in Figure 1A;
Figure 1L is a cross-sectional view of the load
sleeve of Figure 1J taken along line 1L-1L of Figure 1M;
Figure 1M is an end view of the load sleeve of
Figure 1L;
Figures IN is a perspective view of a swivel body of
the top drive shown in Figure 1A;
Figure 10 is a top view of the swivel body shown in
Figure iN;
Figure 1P is a cross-sectional view of the swivel
body shown in Figure 1N;
Figure 1Q is a bottom view of the swivel body shown
in Figure 1N;
Figure 1R is a perspective view, partially cutaway,
of the swivel body shown in Figure 1N;
Figures IS is a perspective view of a swivel body of
the top drive shown in Figure lA;
Figure IT is an end view of a pin for use in the
swivel body shown in Figure 1N;
Figure lU is a cross-section view of the pin shown
in Figure 1T;
Figure 2A is a side view of part of a rig
incorporating the apparatus shown in Figure 1A;
Figure 2B is a top view of the part of the rig shown
in Figure 2A, also showing further pipe storage areas;
Figure 2C is a perspective view of an extension
mechanism of the apparatus shown in Figure 1A, shown in a
CA 02634533 2008-07-08
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retracted position;
Figure 2D shows the extension mechanism shown in
Figure 2C, shown in an extended position;
Figure 2E is a top view of the extension mechanism
shown in Figure 2D in the extended position;
Figure 2F is a side view of part of the torque tube
shown in Figure 2C;
Figure 2G is a schematic view of an apparatus in
accordance with the present invention;
Figure 3 shows the layout of Figures 3A to 3E, which
combine to show a schematic view of a control system for
the apparatus shown in Figure 1A;
Figure 3F is a schematic view of a coolant circuit
for a system in accordance with the present invention.
Figure 4A is a perspective view of part of the top
drive shown in Figure 1A;
Figure 4B is a cross-sectional view of what is shown
in Figure 4A;
Figure 4C is an exploded view of part of the top
drive shown in Figure 1A;
Figure 4D is an enlargement of a gear arrangement of
the top drive shown in Figure 1A;
Figure 4E is a perspective view of part of the
apparatus shown in Figure 1A;
Figure 4F is an exploded view of the part of the
apparatus shown in Figure 4E;
Figure 5A is a perspective view of the gear collar
of the apparatus shown in Figure 1A showing the top of
the gear collar;
Figure 5B is a perspective view of the gear collar
shown in Figure 5A showing the underside of the gear
collar;
CA 02634533 2008-07-08
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Figure 5C is a top view of the gear collar shown in
Figure 5A;
Figure 5D is a front view of the gear collar of
Figure 5A;
Figures 5E and 5F are perspective views of part of
the apparatus shown in Figure 1A;
Figure 6A is a perspective view of the load collar
of the apparatus shown in Figure 1A showing the top of
the load collar;
Figure 6B is a perspective view of the load collar
shown in Figure 6A showing the underside of the load
collar;
Figure 6C is a front view of the load collar shown
in Figure 6A;
Figure 6D is a top view of the load collar shown in
Figure 6A.
Figure 7A is a cross-sectional view of part of the
locking mechanism for the apparatus shown in Figure 1A;
Figures 7B is a perspective view of part of the
locking mechanism shown in Figure 7A showing the top of
the part;
Figure 7C is a perspective view of the part of the
locking mechanism shown in Figure 7A showing the
underside of the part;
Figure 7D is a perspective view of a splined member
of the locking mechanism shown in Figure 7A;
Figure 7E is a perspective view of a gear of the
locking mechanism shown in Figure 7A;
Figure 7F is a perspective view of a pinion gear of
the locking mechanism shown in Figure 7A;
Figure 7G is a perspective view showing part of the
locking mechanism shown in Figure 7A showing the rear of
CA 02634533 2008-07-08
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the locking member;
Figure 7H is a perspective view showing part of the
locking mechanism shown in Figure 7A in place in the top
drive shown in Figure 1A;
Figure 71 is an exploded view of the locking
mechanism shown in Figure 7G;
Figure 8A is a front view of the clamping apparatus
of the apparatus shown in Figure IA;
Figure 8B is a top view of the apparatus shown in
Figure 8A;
Figure 8C is a perspective view, partially cutaway,
of the clamping apparatus shown in Figure 8A;
Figure 8D is a perspective view of an upper leg of
the clamping apparatus shown in Figure 8A;
Figure BE is a front view of the upper leg shown in
Figure 8D;
Figure 8F is a perspective view of an inner leg of
the clamping apparatus shown in Figure 8A;
Figure 8G is a perspective view, partially
cutaway, of the clamping apparatus shown in Figure 8A;
Figure 8H is a perspective view of part of the
clamping apparatus shown in Figure 8G;
Figure 81 is a perspective view of part of the
clamping apparatus shown in Figure 8G;
Figure 8J is a top view in cross-section of the
clamping apparatus shown in Figure 8H;
Figure 8K is a perspective view of a die holder of
the clamping apparatus shown in Figure 8G;
Figure 8L is a perspective view of a liner of the
clamping apparatus shown in Figure 8G;
Figure 8M is a cross-section view of the liner of
Figure 8L;
CA 02634533 2011-01-25
29-
Figures 8N and 80 are perspective views of a piston
of the clamping apparatus shown in Figure 8G;
Figures 8P is an end view and 8Q is a view in cross-
section of the piston shown in Figure 8N;
Figures 8R and 8S are perspective views of parts of
a pipe guide of the clamping apparatus shown in Figure 8;
Figure 8T illustrates alternative cross-sectional
shapes for the legs of the clamping apparatus shown in
Figure 8A (and for corresponding holes receiving such
legs) ;
Figure 8U is a perspective view of a spring holder
of the clamping apparatus shown in Figure 8A;
Figure 8V is a top view of an inner leg of the
apparatus shown in Figure 8A;
Figure 8W to 8Y are perspective views showing
various positions of a torque wrench clamping apparatus
in accordance with the present invention;
Figure 8Z is an exploded view of parts of the torque
wrench clamping apparatus shown in Figure 8W;
Figure 9A is a side view of part of the apparatus
shown in Figure 1A showing an elevator and mechanically
movable bails in a first position;
Figure 9B is a side view of the part of the
apparatus shown in Figure 9A showing an elevator and
mechanically movable bails in a second position;
Figure 9C is a side view of the part of the
apparatus shown in Figure 9A showing an elevator and
mechanically movable bails in a third position;
Figure 10A is a perspective view of a brake drum of
the brake system of the apparatus shown in Figure 1A;
Figure 10B is a perspective view of a brake disc of
the brake system of the apparatus shown in Figure 1A;
CA 02634533 2008-07-08
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Figures 11A is a perspective view of the connection
lock member showing the top of the connection lock
member;
Figures 11B is a perspective view of a connection
lock member showing the underneath of the connection lock
member;
Figure 11C is a top view of the connection lock
member shown in Figure 11A;
Figure 11D is a view in cross-section of the
connection lock member shown in Figure 11A;
Figure 11E is a perspective view of the mud saver
apparatus and saver sub of the apparatus shown in Fig.
1A;
Figure 11F is an exploded view of the mud saver
apparatus and saver sub shown in Figure 11E;
Figure 12A is a perspective view of the crossover
sub of the apparatus shown in Figure 1A;
Figure 12B is a top view of the crossover sub shown
in Figure 12A;
Figure 12C is a view in cross-section of the
crossover sub shown in Figure 12A taken along line 12C-
12C of Figure 12B;
Figure 13 is a perspective view of the bonnet of the
apparatus shown in Figure 1A;
Figure 14A is a perspective view of a load nut of
the apparatus of Figure IA showing a top side of the load
nut;
Figure 14B is a perspective view of the load nut
shown in Figure 14A showing the underneath of the load
nut;
Figures 15A is a perspective view of an inner barrel
of the rotating head of the apparatus shown in Figure 1A;
CA 02634533 2008-07-08
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Figure 15C is a view in cross-section of the inner
barrel shown in Figure 15A taken along line 15C-15C of
Figure 15E;
Figure 15D is a view in cross-section of the inner
barrel shown in Figure 15A taken alone line 15D-15D of
Figure 15E;
Figure 15E is a view in cross-section of the inner
barrel shown in Figure 15A;
Figure 15F is a view in cross-section of the inner
barrel shown in Figure 15A taken along line 15F-15F of
Figure 15E;
Figure 15G is a perspective view of an outer barrel
of the rotating head;
Figure 15H is a side view in cross-section of part
of the apparatus shown in Figure 1A;
Figure 16A is a perspective view of a washpipe
assembly of the apparatus shown in Figure 1A;
Figure 16B is a side view, partially in cross-
section, of the washpipe assembly shown in Figure 16A;
Figure 17A is a side view of an access platform of
the apparatus shown in Figure 1A;
Figure 17B is a front view, Figure 17C is a front
perspective view, Figure 17D is a rear perspective view,
Figure 17E is a bottom view, and Figure 17F is a top view
of the access platform shown in Figure 17A;
Figures 17G and 17H are side views of the access
platform shown in Figure 17A connected to the top drive
shown in Figure 1A in a first and second positions
respectively;
Figure 171 is a perspective view of a guard member
shown in Figure 17A showing the front of the guard
member;
CA 02634533 2010-08-20
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Figure 17J is a perspective view of the guard member
shown in Figure 171 showing the rear of the guard member;
Figure 18A is a perspective view of a motor dam for
use with the motor of the top drive shown in Figure 1A;
Figure 18B is a view in cross-section of the motor
dam shown in Figure 18A;
Figure 19A is a perspective view of a slinger for use
with the apparatus shown in Figure 1A;
Figure 19B is a view in cross-section of the slinger
shown in Figure 19A;
Figure 20A is a perspective view of a slinger for use
with the apparatus shown in Figure 1A;
Figure 20B is a view in cross-section of the slinger
shown in Figure 20A;
Figure 21 is a top view of a wear guide for use with
the apparatus shown in Figure 1A;
Figure 22 is a view in cross-section of the wear
guide shown in Figure 21;
Figure 23A is a side view of a connection apparatus
for use in suspending the apparatus shown in Figure 1A;
Figure 23B is a view in cross-section of the
connection apparatus shown in Figure 23A;
Figure 23C is a perspective view of a connection
apparatus of the connection apparatus shown in Figure 23A;
Figure 23D is a perspective view of a part of the
connection apparatus shown in Figure 23A;
Figure 23E is a side view in cross-section of the
part of the travelling connection apparatus shown in
Figure 23D;
Figure 23F is a front (or rear) view in cross
CA 02634533 2008-07-08
- 33-
section of the part of the connection apparatus shown in
Figure 23D;
Figure 23G is a bottom view of the part of the
connection apparatus shown in Figure 23D;
Figure 23H is a perspective view of the part of the
connection apparatus shown in Figure 23D showing the
underneath of the part;
Figure 24A is a perspective view of a spacer plate
of the apparatus shown in Figure 1A;
Figure 24B is a view in cross-section of the spacer
plate shown in Figure 24A;
Figure 25 is a perspective view of the spacer plate
shown in Figure 24A showing the underneath of the spacer
plate;
Figures 26A and 26B are perspective views of a link
for use with a system as in Figure 1A;
Figure 26C is a side view and Figure 26D is a front
view of the link shown in Figure 26A;
Figure 26E is a top view and Figure 26F is a bottom
view of the link shown in Figure 26A;
Figures 27A to 27C are side views of part of the
apparatus shown in Figure 1A indicating steps in a method
of operation;
Figures 27D to 27F are top views in cross-section of
the parts of the apparatus shown in Figure 27A to 27C
indicating the steps in the method shown in Figures 27A
to 27C respectively;
Figures 28A and 28B are perspective views of a
building for use with the apparatus shown in Figure 1A;
Figure 28C is an end view of the building shown in
Figure 28A with doors of the building open;
Figure 28D is a top view of the building shown in
CA 02634533 2008-07-08
- 34-
Figure 28A with a roof of the building removed;
Figure 28E is a perspective view of a carrier skid
for use with the building shown in Figure 28A;
Figure 29A is a perspective view of a guard for use
in the apparatus as shown in Figure 1A showing a front
and a first side of the guard;
Figure 29B is a perspective view of the guard shown
in Figure 29A showing the rear and the first side of the
guard;
Figure 29C is a perspective view of the guard shown
in Figure 29A showing the rear and second side of the
guard;
Figure 29D is a plan view of the guard shown in
Figure 29A taken from the first side of the guard;
Figure 29E is a plan view of the guard shown in
Figure 29A taken from the rear of the guard;
Figure 29F is a plan view of the guard shown in
Figure 29A taken from the second side of guard;
Figure 29G is a top plan view of the guard shown in
Figure 29A;
Figure 29H is a bottom view of the guard shown in
Figure 29A;
Figure 30A is a perspective view of a guard for use
in the apparatus shown in Figure 1A showing the front and
a first side.
Figure 30B is a perspective view of the guard shown
in Figure 30A showing the front and a second side of the
guard;
Figure 30C is a perspective view of the guard shown
in Figure 30A showing the first and second sides and the
rear of the front of the guard;
Figure 30D is a plan view of the guard shown in
CA 02634533 2008-07-08
- 35-
Figure 30A taken from the first side of the guard;
Figure 30E is a plan view of the guard shown in
Figure 30A taken from the rear of the guard;
Figure 30F is a plan view of the guard shown in
Figure 30A taken from the second side of the guard;
Figure 30G is a top view of the guard shown in
Figure 30A;
Figure 30H is a bottom view of the guard shown in
Figure 30A;
Figure 31A is a top view of the top drive shown in
Figure 1A and a reaction frame in a first step of
operation;
Figure 31B is a top view of the top drive shown in
Figure 1A and the reaction frame shown in Figure 31A in a
second step of operation;
Figure 31C is a side view of part of the reaction
frame shown in Figure 31A;
Figure 31D is a perspective view of a stand/support
for use with the top drive shown in Figure 1A;
Figure 31E is a perspective view of part of the
reaction frame shown in Figure 31A;
Figure 31F is a perspective view of part of the
reaction frame shown in Figure 31C showing the rear of
the part;
Figure 31G is a perspective view of the part of the
reaction frame shown in Figure 31F showing the front of
the part;
Figure 31H is a perspective view of part of the
reaction frame shown in Figure 31C;
Figure 32A is a front view of part of the apparatus
shown in Figure 2A shown in a first position;
Figure 32B is a front view of the part of the
CA 02634533 2008-07-08
- 36-
apparatus shown in Figure 32A shown in a second position;
Figure 32C is a side view of the part of the
apparatus shown in Figure 32B;
Figure 32D is a perspective view of part of the
apparatus shown in Figure 32A;
Figure 32E is a perspective view of part of the
apparatus shown in Figure 32A;
Figure 33A is a top view of a seal assembly for use
in the apparatus shown in Figure 1A;
Figure 33B is a side view in cross-section of the
seal assembly shown in Figure 33A;
Figure 33C is an enlarged side view in cross-section
of part of the seal assembly shown in Figure 33B;
Figure 34A is a front view with some hidden parts
shown a seal assembly;
Figure 34B is an enlargement of part of the seal
assembly shown in Figure 34A;
Figure 35A is a side view of a link for use in the
apparatus shown in Figure 1A in a first position of use;
Figure 35B is a front view of the link shown in
Figure 35A;
Figure 35C is a front view of the link shown in
Figure 35A in a second position of use;
Figure 35D is a top view of the link shown in Figure
35A;
Figure 35E is a perspective view of the link shown
in Figure 35A in a first position of use;
Figure 35F is a perspective view of the link shown
in Figure 35A in a second position of use; and
Figure 35G is a bottom view of the link shown in
Figure 35A.
Figs 1A to 1D show an apparatus generally identified
CA 02634533 2008-07-08
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by the reference numeral 10. The apparatus 10 has a
swivel body 12 suspended on links 14 from a becket 16.
The becket 16 is connected to a travelling block, or a
connection apparatus of the type shown in Figure 23 could
be used to suspended the top drive from a part of a
derrick in which the apparatus is situated in use. A
gear system 20 is mounted on a spacer plate 22 which is
supported by the swivel body 12. Optionally, a
dehumidifier system (not shown) dehumidifies the
apparatus.
A hollowbore alternating current permanent magnet
motor 30 is coupled to the gear system 20. Any suitable
permanent magnet motor may be used; for example, but not
limited to, a commercially available alternating current
hollow bore permanent magnet motor model TERA TORQ (TM)
from Comprehensive Power Ltd., Boston, Massachusetts
(which motor is supplied with a control system and which
has associated computer system software and controls; and
which can be programmed so that the motor itself can
serve as a brake). A brake system 40 connected to the
motor 30 is within or covered or protected by a bonnet 44
through which extends a gooseneck 46 connected to a kelly
hose 7 which forms part of a service loop 48. Drilling
fluid flows through Kelly hose 7 in certain stages of
use. An extension mechanism 98 provides substantially
horizontal displacement of the top drive 1 (see Figures
2C, 2D, 2E). The emergency brake system 40 can operate
either selectively or automatically, for example, the
driller has an emergency brake button on the driller's
panel 141.
Referring to Figure 1C and 1H, the motor 30 has a
splined output shaft 32 which drivingly meshes with a
CA 02634533 2008-07-08
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splined portion 26 of the gear system 20 which has a
splined portion 224 that mates with a splined portion 52
of a quill 50. A flange 54 of the quill 50 bears string
load weight and rotates on a main bearing system 56 in
the swivel body 12. The quill 50 extends through the
motor 30, the gear system 20, the spacer plate 22, the
swivel body 12, a locking mechanism 60, a load collar 70,
and a rotary seal 80. A lower end 58 of the quill 50 is
threadedly connected to a mud saver apparatus 90 which
itself is connected to a saver sub 92. A clamping
apparatus 100 for selectively gripping or clamping
tubulars is suspended from a load collar 70 which is
attached to a static part of the top drive 1. Bails 72
suspend an elevator 74 from the load collar 70. Keys 395
in key slots 396 (see Figure 11) releasably connect the
end of the quill 50 to a connection lock member 340
(Figure 11A) as described below to insure a connection
between the quill 50 and mud saver apparatus 90 is
maintained.
A counterbalance system 110, which can hold the
weight of the entire top drive 1 and associated tubulars
to be stabbed during stabbing of tubulars, includes two
load compensators 112 each'with an upper end connected to
a link 14 and with a lower end connected to the swivel
body 12. Lower ends of the links 14 have elongate
openings 14c which are sized and configured to permit a
range of movement in a vertical plane (for example about
15cm (6 inches)) with respect to pins 13 that maintain
the links 14 in the swivel body 12. The load compensator
cylinders 112 may be hydraulic, and preferably comprises
an accumulator 116 which allows stabbing to be load
balanced to match the load of the top drive and tubular
CA 02634533 2008-07-08
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or stand of tubulars to be stabbed, to facilitate
stabbing into a box of a tubular in a string held in a
spider in the rig floor. The weight is preferably
counterbalanced and thus the chances of the thread on the
pin of the tubular to be stabbed colliding and with the
thread of the box being stabbed into is minimised. Thus
when the swivel body 12 supports the brakes, motor, gear
system and bonnet counter balancing can be conducted.
Retainer plates 399 secured to the swivel body 12 with
bolts 399a releasably retain the pins 13 in place in the
recesses 12b (i.e. the pins 13 do not take up all the
space within the link openings). Each load compensator
112 includes a piston/cylinder assembly 114. The
cylinders are balanced using charged accumulators 116
located on the links.
A movable bail apparatus 120 provides selective
tilting of the bails 72 and thus selective movement and
of the elevator 74 and movement of a tubular or stand of
tubulars supported by the elevator 74 to and away from a
wellbore centerline. A shaft 120a passes through the
load collar 70 and the bails 72 (see Figure 7I). Bail
retainers 404 retain the bails 72 on the load collar 70
(Figure 8A). The movable bail apparatus 120 has
hydraulic cylinders 128 interconnected pivotably between
ears 128a of the load collar 70 and arms 122. Each
connector 124 is pivotably connected to a lower end of an
arm 122 and to a clamp 126 which is clamped to a bail 72.
Optionally, roller pins 127 extend through the clamps 126
to facilitate movement of the bails 72 within the clamps
126.
Guards 73 and 390 are on sides of an access platform
130 (see also Figures 29A - 29H and 30A - 30H). The
CA 02634533 2008-07-08
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access platform 130 is releasably connected to a rear
guard 454 at its top and pivotably at its lower portion
to the guards so that it can pivot and be lowered to
provide a platform on which personnel can stand to access
various components on the rear guard. Optionally, the
access platform 130 may have an indented portion 132 for
facilitating the placement of tubulars thereon and for
facilitating movement of tubulars on the exterior of the
access platform 130.
The top drive 1 can be movably mounted on a beam 82
(or "torque tube"). Horizontal displacement is provided
by the extension mechanism 98 which includes a torque
bushing 98a. The extension mechanism 98 with the top
drive 1 attached thereto is movable vertically on the
beam 82. Optionally, the motor is a four quadrant drive
so it can be used to regenerate power.
Figures 1J to IM show a load sleeve 170 with four
channels 170a therethrough. These channels extend to a
lower end of the load sleeve 170. At the bottom, each of
the four channels is in fluid communication with
corresponding channels in a rotating head 80 (see, for
example Figure 15A). The rotating head 80 is connected
on the lower end of the load sleeve 170. Via the fluid
channels in the load sleeve and the corresponding
channels in the rotating head 80, hydraulic fluid under
pressure provides power and/or lubricating for
apparatuses below the rotating head; including, for
example movable bail apparatus, the clamping of the
clamping apparatus 100, the up/down movement of the
clamping apparatus 100, the elevator 74 when it is
hydraulically powered, and the mud saver apparatus 90.
This fluid also flows via appropriate channels to a
CA 02634533 2008-07-08
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generator system 240 located at or near the level of pipe
handling apparatus, as described below, which produces
electrical power for directional valves that control flow
in the various channels. In one aspect the generator
system 240 is a minigenset. The minigenset in one aspect
is hydraulically powered (with pressurized hydraulic
fluid or water/glycol mixture). A flange 170c is
connected to or formed integrally of a body 170d. A
threaded end 170e threadedly mates with corresponding
threads in a load nut. The flange 170c is bolted to the
swivel body 12. In one aspect when the movable bail
apparatus elevator 74 has received and is holding a
tubular or a stand, the cylinder assemblies 128 are under
a relatively heavy load. A directional valve 260 allows
fluid to flow from the lines connected to the cylinder
assemblies 128 thereby relieving the pressure therein and
allowing the bails 72 to move block ("float" to vertical,
see "LINK TILT FLOAT," Figure 3, "link tilt" in Figure 3
refers to the mechanically movable bails.
Figures IN to 1P show one embodiment for a swivel
body 12. Figure IN shows one side and end (the other
side and end are like the side and end shown). The
swivel body 12 has two holes 12a for ends of the links 14
and two holes 12b for the removable pins 13. The holes
12b may have bushings 12e. In one particular aspect the
bushings 12e are phenolic bushings, but they may be made
of any suitable material, including, but not limited to,
brass, bronze, zinc, aluminum and composite materials.
The bushings 12e facilitate pin 13 emplacement and
removal and the bushings 12e are easily replaced. A
channel 12c extends through the swivel body 12 and
receives and holds a main bushing 56. As shown the pins
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13 are stepped with portions 13a, 13b, 13c and phenolic
bushings 13d and 13e may be used with the pins 13 (see
also Figure 4F). Drain port or outlet ports 12s, 12t
(plugged with removable plugs) permit lube oil flow
through and permit the draining of oil from the system.
Port 12t allows lube oil through to lubricate the lower
quill stabilizer bearing 57 via access via the load
sleeve 170. Figure 1T shows a pin 13p useful as a pin 13
in Figure 1R. The pin 13p has a body with a hole 13h
leading to a channel 13f for introducing air into and
through the pin 13p, for example to assist in insertion
of the pin 13p into a swivel body and to facilitate
removal of the pin 13p from a swivel body. The pin 13p
has a hole 13i leading to a channel 13g for introducing
grease into and through the pin 13p to facilitate its
insertion into and removal from a swivel body. Figure 1T
shows a pin 13p useful as a pin 13 in Figure 1R. The pin
13p has a body with a hole 13h leading to a channel 13f
for introducing air into and through the pin 13p, for
example to assist in insertion of the pin 13p into a
swivel body and to facilitate removal of the pin 13p from
a swivel body. The pin 13p has a hole 13i leading to a
channel 13g for introducing grease into and through the
pin 13p to facilitate its insertion into and removal from
a swivel body.
The holes 12a may be circular, but are shown as
rectangular to inhibit turning of the links 14 in the
holes. The holes may be any suitable shape to inhibit
link turning.
Figures 2A and 28 illustrate one installation of the
apparatus 10 in accordance with the present invention in
a derrick 140. The top drive 1 is suspended from a
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connection apparatus 18, which is suspended from the
derrick 140 in a typical manner. Although it is within
the scope of the present invention to use a standard
block and hook for hooking a standard becket, the
connection apparatus 18 dispenses with the common
swiveling hook. As shown in Figure 2A, the elevator 74
is supporting a tubular stand 142 which includes two
pieces of drill pipe 143. The stand 142 has been moved
from a monkey board 145 with multiple made-up stands 149
to a position axially aligned with a welibore 147. A
mousehole 144 may be used, for example to make stands. A
driller controls drilling from a driller's panel 141.
Optionally, the system includes an emergency brake system
and/or an emergency shut down device and, optionally,
either or both are controllable from the panel 141. In
one aspect, if power to the system is lost, a valve (in
the system of Figure 171; see "SHUT-OFF VALVE", Figure 3)
opens and pressure in a corresponding accumulator is
released thereby closing the system brakes.
Figure 2G shows schematically a top drive 10a in
accordance with the present invention (which may be any
top drive in accordance with the present invention as
disclosed herein, but without a connection apparatus in
accordance with the present invention) with a travelling
block T, hook H, and becket B (each of which may be a
suitable known block, hook, and/or becket, respectively).
The flange 54 of the quill 50 rests on the main
bearing 56, a thrust bearing, for example a V flat type
thrust bearing which has multiple tapered rollers 57.
The upper surface of the flange 54 abuts an upper thrust
bearing 59 located in a suitable recess 24 of the spacer
plate 22 (see for example Figures 1C, 1D, 1G, 1H) . The
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quill 50 has an upper part 51 in fluid communication with
the gooseneck 46 via a wash pipe 374. In one particular
aspect the main bearing 56 is a V-type thrust bearing
which accommodates eccentricity, if present, in the quill
50 and is self-cleaning.
The swivel body 12 and associated structures provide
dual load paths (which is desirable for reducing
maintenance requirements. Drilling loads through the
quill 50 travel through the main bearing 56, through the
swivel body 12, to the links 14, to the becket 16 and
then to the connection apparatus 18. Tripping loads (or
"string loads" imposed on the system by tubulars being
supported by the apparatus) are imposed on the bails 72
through the elevator 74, then onto the load collar 70 and
the load sleeve 170, to the swivel body 12, to the links
14 and to the becket 16. This dual-load path allows for
rotation of the clamping apparatus 100 whether the quill
50 is rotating or not. The tripping loads are not
imposed on the quill 50, but are transferred via the
tripping load path around the quill 50 through the swivel
body 12 and links 14. In certain aspects the gear system
and motor are not subjected to loads (for example the
drill string load). Thus in scaling up the system (for
example from a 150 ton unit to a 1500 ton unit) the
swivel housing (body) is scaled up to accommodate a
larger load while the identical gear system (which is not
in the swivel housing) and motor are employed.
In one particular aspect the permanent magnet motor
is a Model 2600 TERA TORQ (TM) motor commercially
30 available from Comprehensive Power Ltd. which is a
liquid-cooled AC permanent magnet hollow bore motor which
generates 700 HP and operates at a maximum speed of 2400
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RPM. The motor has axial bearings and a splined output
shaft and is designed to hold drill string torque at full
stall (at "full stall" motor RPM's are zero) or while
engaged in jarring (for example using shock loads for
various purposes) A central hollow bore 30a extends
through the motor 30 from top to bottom through which
fluid, for example drilling fluid, can flow through the
motor. In one particular aspect such a motor is supplied
with a Variable Frequency Drive control system (in one
aspect, drive system 531, Figure 28D) which is a liquid-
cooled modular electronic unit with modules that can be
changed in about five minutes. Such a system can
translate generator horsepower at over 90% efficiency and
can run in temperatures of -40 C to 60 C and in high (for
example up to 100%) humidity.
In one particular aspect the gear system 20 includes
a single speed planetary gear reduction system with gear
combinations providing a 9.25:1 ratio (or a 12:1 ratio)
and with a liquid-cooled gear box which is fully
lubricated down to 0 RPM. The system has a splined input
shaft 26 for mating with the splined motor output shaft
32 for transmitting power to the quill 50.
The compensator system 110 permits a soft landing
for a tubular when the top drive is lowered to stab the
tubular into a connection.
In one particular aspect the mud saver apparatus 90
is a commercially available double ball internal blowout
preventer system from R Folk Ventures of Calgary, Canada
which has two internal blowout preventers and which is
rated to 15,000 psi. An upper valve is hydraulically
actuated by an actuator mounted on the valve and a lower
valve is manually opened and closed. Alternatively, a
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Hi-Kalibre mud saver apparatus (commercially available)
can be used instead of this mud saver apparatus.
Figures 4A to 4F show, among other things, the
interconnection of the motor 30 and gear system 20 and
the respective position of these items, the bonnet 44,
the brake system 40, the spacer plate 22, the swivel body
12, the quill 50, and the load sleeve 170. Within the
lower part of the bonnet 44 are three calliper disc
brakes 180 (for example commercially available systems)
which act on a brake disc 183 (see Figure 10B) which is
secured to a brake hub 41 (see Figure 10A) secured to the
motor 30. Shims preload the bearing 59, a pre-load that
does not need to be re-set due to a shoulder structure of
the spacer plate 22.
Figure 4D shows a gear system 20 which has a housing
480 from which extends a sight glass apparatus 481 for
checking fluid level in the system 20 which includes a
breather apparatus 482 that allows atmospheric pressure
above the lube system to encourage downward gravitational
flow. The sight glass apparatus 481 may be located at
any suitable desired level (for example, but not limited
to, coming out of a spacer plate 22 on top of the gear
box). An input spline 26 drivingly meshes with the
correspondingly splined output shaft 32 of the motor 30.
A first sun gear 483 rotates, for example at 2400 rpm and
three planet gears 484 on stubs 485a of an upper carrier
485 rotate around the first sun gear 483. Five lower
planet gears 486 rotatably mounted on stubs 487a of a
lower carrier 487 encircle a second sun gear 488. An
output spline 489 drivingly meshes with the splined
portion 52 of the quill. In one aspect the output spline
rotates at 259 rpm when the first sun gear 483 rotates at
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2400 rpm. An optional seal 491 seals an interface
between the gear system 20 and the motor 30. Bolts
through holes 492 connect the system 20 to the spacer
plate 22. The first sun gear 483, driven by the motor
30, drives the planet gears 484 which drive the upper
carrier 485, which rotates the second sun gear 488 which
drives the five lower planet gears 486, which drive the
lower carrier 487, which drives the output spline 489.
The output spline 489 rides on bearings 493. Magnetic
plugs 494 (one shown) collect metal debris. An upper
bearing 495 is lubricated through a port 496 and a top
mechanical seal 497 (which prevents oil from going up
into the motor 3D) is located in a top member 498
connected to and rotatable with the sun gear 483. Bolts
in bolt holes 499 (one shown; twenty four bolts used in
one aspect) connect the gear system 20 to the motor 30.
An oil path 501 allows oil to lubricate the planet gears
and their bearings. The gear system may be a 3 stage/2
speed system or, as shown, a 2 stage/l speed system.
The locking mechanism 60, described in detail below
with reference to Figure 7A to 7E, is bolted beneath the
swivel body 12, supported on the load collar 70, and
provides releasable locking of the clamping apparatus 100
in a desired position. In one particular aspect the
clamping apparatus 100 is operable throughout a full 360
in both directions, at about 4 RPM. In one particular
aspect the clamping apparatus 100 is driven by four low
speed high-torque motors 190 which are fixed to a movable
toothed lock plate 191 which is suspended by two
hydraulic cylinders 192 which selectively move the lock
plate 191 up and down (for example in one aspect with a
range of motion of about 4.5cm (1.75 inches)) to engage
CA 02634533 2008-07-08
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and disengage a rotate gear 193 whose rotation by pinion
gears 69 located in pinion gear recesses 69c (driven by
the motors 190) results in a rotation of the clamping
apparatus 100. Shafts of the motors 190 are in channels
69d of the pinion gears 69. The rotate gear 193 is
bolted to the top of a gear collar 194 which itself is
bolted on top of the load collar 70. A lock guide 62
(Figure 7D), bolted to and beneath the swivel body 12,
has a splined portion 63 which is always in mating
engagement with a corresponding splined portion 195 of
the lock plate 191, so that lowering of the lock plate
191 results in engagement of the rotate gear 193 with the
locking plate 191 and thus in locking of the clamping
apparatus 100 preventing its rotation when the hydraulic
cylinders 192 have lowered the lock plate 191 so that its
inner teeth 196 engage teeth 197 of the rotate gear 193.
The pinion gears 69 (Figure 7F) are in contact with the
rotate gear 193 whether the clamping apparatus 100 is
locked or not and rotation of the pinion gears 69 by the
motors 190 results in rotation of the clamping apparatus
100. Figure 7A shows the lock engaged in a locked
position, i.e. the clamping apparatus 100 cannot rotate.
When the locking mechanism 60 is unlocked, the pinion
gears 69, turned by the motors 190, turn the rotate gear
193, for example to reposition the clamping apparatus 100
or the elevator 74. In the locked position the quill 50
can still rotate, but the clamping apparatus 100 cannot.
Optionally, to facilitate tooth engagement, the teeth 195
can have tapered lead-ins 195a and the teeth 197 can have
tapered lead-ins 197a. These profiles insure
synchronization between the gear 196 and the rotate gear
193. The gear 196 has teeth for the great majority of
CA 02634533 2008-07-08
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its circumference providing more structure and more
strength to hold the clamping apparatus 100 and the
movable bail apparatus 120 and prevent rotation of the
clamping apparatus 100 in a locked position. Cups 69a
maintain the pinion gears 69 in recesses 69c. The lock
guide 62 has four ports 62q to 62t each aligned with a
channel 170a of the load sleeve 170 so that hydraulic
fluid from the upper hydraulic manifold 452 can flow to
and through the load sleeve 170 to the rotating head 80.
Suitable hoses and/or tubing conduct fluid from the upper
hydraulic manifold 452 to the lock guide ports 62q to
62t.
The gear collar 194 (Figures 5A, 5B) is bolted on
top of the load collar 70 with bolts 194a. Grease to
lubricate the wear sleeve 62 and the load collar bearing
67 is introduced into grease ports 194d. When the lock
plate 191 has been lowered to engage the rotate gear 193
to prevent rotation of the clamping apparatus 100 and
elevator 74, the quill 50 can still rotate. Optionally
the hydraulic cylinders 192 can have springs and/or
spring washers 198 to provide a fail safe lock, for
example when there is a loss of power to the hydraulic
cylinders 192. Depending on the size, configuration, and
disposition of interengaging teeth, the clamping
apparatus 100 can be locked at desired circumferential
increments. In one particular aspect, for example with
components as shown in Figures 7A to 7E, the clamping
apparatus 100 can be locked every 4 degrees. Such a
range of movement - a full 360 - allows the lower pipe
handling equipment to thread tubulars together. In one
aspect (see Figures 5E, 5F) the load collar 70 and the
gear collar 194 are a single integral piece 194p (for
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example made by casting).
A rotating head 80 provides hydraulic power to the
rotatable clamping apparatus 100. This hydraulic power
operates a generator 240 mounted in a lower electrical
junction box 250 and valves 260 (see, for example Figure
8A). In one aspect the generator 240 is a mini
generator, for example, but not limited to, a
commercially available mini generator set from
Comprehensive Power Ltd. of Boston, Massachusetts. In
one aspect the junction box 250 is a zone 0 rated
junction box. The generator 240 provides electric power
to directional valves 260 on the lower hydraulic manifold
400 mounted on an upper leg of the clamping apparatus
100. The generator 240 is powered by hydraulic fluid
from the rotating head which powers the generator. Also,
optionally, the clamping apparatus 100 includes digital
signal processor card systems 256a, 256b, 256c (lower
electrical junction box 250), 256d, each with its own RF
antenna. A Digital Signal Processing (DSP) system 256a
(shown schematically in Figure 2A), is located in the
driller's panel 141; a DSP system 256b, is on the rear
guard 454 in the upper electrical box 450; and a DSP
system is in the lower electrical junction box 250 on a
lower leg of the clamping apparatus 100; and/or a DSP
system 256d in the building 160. These DSP systems
provide communication between the top drive's components
[for example the mud saver apparatus 90, extension
mechanism 98, motor 30, clamping apparatus 100, elevator
74, (when powered) , brake system 40, lock system 60] and
the driller; and, in one aspect, with personnel in the
building 160.
Figures 8A to 8C and 8W to 8Z illustrate one
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embodiment of the clamping apparatus 100 for selectively
clamping tubulars, for example pipe or casing. Top ends
of the outer legs 285 of the clamping apparatus 100 are
connected to connection structures 194b and 194c of the
gear collar 194 with pins 285a and with pins 285b to
connection structures 70a of the load collar 70; and the
bottom ends of the inner legs 283 are bolted to a body
284 (including mounts 293). The inner leg 283 and outer
leg 285 are made from box section, which may be steel or
a plastics or composite material. The box section
facilitates torque transfer when spinning and torquing
joints with the clamping apparatus. Bolts 283a bolt
plates 284a and ends of leg 283 to the mounts 293. Each
leg has two parts, an inner (lower) part 283 and an outer
(upper) part 285. The inner parts 283 move within the
outer parts 285 to provide a telescoping action that
permits upward and downward motion of the clamping
apparatus 100 (for example in one aspect with an up/down
travel range of 72cm (28.5")). A spring or springs 286
within each leg on a spring mount 289 so that when
breaking a connection the springs compensate for thread
travel; and when making a connection the vacuum in
assemblies 282 compensates for upward travel of the
threads. In one particular aspect (see Figure 8C) stacks
of belleville springs 286 in each leg are mounted on rods
289a of the spring mount 289 which is connected to the
inner leg.
The body 284 has dual opposed halves 288, 289 pinned
together with removable pins 291 so that the body 284 can
be opened from either side with the structure on the
unopened side serving as a hinge. Also, both halves can
be unpinned (removing the pins 291) permitting the legs
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to be moved apart (following removal of the pins 285b)
allowing access to items on the legs (for example the
lower electrical junction box 250 and the lower hydraulic
manifold 400) and to other components of the apparatus.
In certain aspects the two halves are identical
facilitating replacement and minimizing required
inventory. Each inner leg has a piston/cylinder assembly
282 which receives hydraulic power fluid via an inlet
282c from the lower hydraulic manifold 400. Each
assembly 282 has a hollow cylinder 282a and an extensible
rod 282b which provides the range of movement for the
legs. Figures 8W to 8Y show different positions of the
clamping apparatus 100.
A pair of jaws 280 of the clamping apparatus 100
(see Figures 8G to 8Q) are provided for selectively and
releasably clamping a tubular. Each jaw 280 has a piston
281 movably disposed in a liner 292 in a housing 293.
Each housing 293 has a plurality of ears 294 with holes
295 therethrough for receiving the pins 291. Connected
to each piston 281 with bolts 299c (in holes 299d of the
pistons 281) is a die holder 297 with recesses 298 for
releasably receiving and holding die mounts 299 with dies
301. In one aspect the liner 292 is made of steel or
other suitably hard material and is replaceable.
Lubricating grease is applied through grease fittings
299a (one shown) and pins 299b (one shown) limit rotation
of the die holders 297. The gear collar 194 is connected
to the legs 285 with connectors 285g and the load collar
is connected to the legs 285 with connectors 2851.
Optionally, a groove or grooves are provided on the
interior surface of the housing 293 for seals to seal the
housing 293/liner 292 interface instead of or in addition
CA 02634533 2008-07-08
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to the grooves for carrying seals on the liner 292 (see
Figure 8M).
Hydraulic fluid under pressure from the rotating
head 80 supplied from the lower hydraulic manifold 400 at
a rear 302 of each piston 281 flows into a "CLOSE" port
304 to clamp a tubular. To release a tubular, hydraulic
fluid is supplied to an "OPEN" port 306. Dotted lines
687 indicate the lines between the rotating head 80 and
the lower hydraulic manifold 400. One of the lines 687
may be a spare line which is plugged shut until needed.
Power cables 688 convey electrical power to the lower
electrical junction box 250. Gland connectors may be
used for connections. This fluid pushes against a piston
opening surface 307 to move the piston 281 and its
associated die apparatus away from a tubular resulting in
unclamping and release of the tubular. Fluid enters (or
leaves) the ports 304, 306 and fills behind the pistons
to clamp onto a tubular or other item. As fluid enters
one port, fluid leaves the other port. Also, in one
aspect fluid flows to (and from) both pistons
simultaneously for balanced clamping and unclamping.
Directional valves 260 in the lower hydraulic manifold
400 control flow to and from the ports 304, 306. A
recess 285m receives and holds a corresponding projection
member (not shown) of the mud saver apparatus 90 to
insure that the mud saver apparatus 90 rotates with the
clamping apparatus 100.
In one aspect the clamping apparatus 100 develops
sufficient torque to break connections involving the
quill 50 and the mud saver 90 and a saver sub 290; and to
make/break tubular connections between the saver sub 290
and tubulars. In one particular aspect a clamping
CA 02634533 2008-07-08
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apparatus 100 as shown in Figures 1C and 8A has a
downward thread feed of about 15cm (6") against the
springs 286; an upward range of movement of about 18cm
(7") against an hydraulic cylinder vacuum in the
cylinders 282; and an up-down travel range when unclamped
of about 72cm (28.5"). By using two spaced-apart legs
instead of a single support to support the clamping
apparatus 100, relatively thinner legs may be used to
accommodate the same amount of torque as a prior art
single-leg support and, with the present invention,
twisting is inhibited and decreased as compared to a
single-leg support (for example in certain aspects a
single leg of a single-leg prior art system is more than
twice the thickness of each of the two legs disclosed
herein), but the two legs are sufficient to handle the
makeup/breakout torques produced (for example up to
81,300 Nm (60,000 ft. lbs) in some embodiments).
Providing relatively thinner legs also means that the
overall area occupied by the clamping apparatus 100 is
reduced, thus permitting the clamping apparatus 100 in
rotation to require a smaller compact space for
operation. By pulling both pins 291, the halves of the
gripper system can be separated and moved apart from each
other. The range of clamping apparatus up/down movement
with corresponding clamping locations allows the clamping
apparatus 100 to clamp onto the mud saver apparatus 90,
or the saver sub 290 to assist in the breaking of the
quill/mud-saver-system connection, the mud-saver-
system/saver sub connection or a connection between a
tubular and the saver sub.
In one particular aspect a clamping apparatus 100 as
shown in Figure 1C and 8A with a die holder 297 that is
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about 3cm (1.25 inches) wide and dies 301 measuring 15cm
(5 3/4") long x 1.6cm (5/8") thick, a range of pipe
between 9cm (3.5") (for example tool joints) and 24cm
(9.5") (for example collars) can be handled. In one
particular aspect the die mounts 299 are swivel die
mounts which facilitate the system's ability to
accommodate a range of tubular diameters; but it is
within the scope of this invention to use non-swivelling
die mounts.
A pipe guide 310 is connected to the bottom of the
body 284. In one aspect the pipe guide 310 includes two
halves 311 (see Figures 8R, 8S) with tapered surfaces 312
to facilitate tubular entry into the clamping apparatus
100. Pins 313a through holes 313 in the halves 311 and
through holes 316 in ears 315 of the mounts 293
releasably secure the halves 311 to the mounts 293.
Safety chains 314 releasably connect to connectors 317 on
the mounts 293 and to connectors 317a on the body 284
prevent the clamping apparatus 100 from falling if it is
inadvertently released from the legs, grabbed, pulled on,
or pulled up with the top drive. Legs 283, 285 may be
chained together at connections 283d, 285d. Safety
chains 314a secure top leg parts to bottom leg parts.
It is within the scope of this invention for the
legs 282 to have a circular cross-sectional shape. In
one aspect, as shown in Figures 8A to 8F, the inner legs
283 have a rectangular cross-sectional shape 322 which
prevents them from rotating within correspondingly shaped
openings 321 in the outer legs 285. This non-rotation
feature is desirable because it inhibits twisting of the
legs and, thereby twisting of the clamping apparatus 100.
It is within the scope of the present invention to
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achieve this non-rotation function with legs of non-
circular cross-section, for example inner legs with non-
circular shapes 323-329 as illustrated in Figure 8T.
Figure 9A shows the bails 72 suspending the elevator
74 beneath the clamping apparatus 100. The movable bails
apparatus known as a "link tilt system" 120 is not
actuated. As shown in Figure 9B, the movable bails
apparatus 120 has been actuated with hydraulic fluid from
the rotating head 230 applied to the piston/cylinder
assemblies 128 to extend the piston 121 moving the arms
122 to move the bails 72 and elevator 74 away from the
clamping apparatus 100. As shown in Figure 9C, the
piston 121 has been retracted, resulting in the arms 122
moving the bails 72 and elevator 74 in a direction
opposite to the direction of movement shown in Figure 9B.
Roller pins 127 within the clamps 126 facilitate link
movement with respect to the clamps 126. In one
particular aspect such a bi-directional link tilt system
can be tilted in one direction toward a V-door of a rig
to more easily accept a stand of pipe from a monkey
board, and in the other direction toward the rig, moving
the elevator out of the way of a drill string and top
drive, to permit drill down closer to a rig floor since
the elevator is moved out of the way. In one particular
aspect, the link tilt system 120 can move the bails 72
and elevator 74 thirty degrees toward the V-door and, in
the other direction, fifty degrees toward the mast. The
bails 72 and the arms 122 lie external to the clamping
apparatus 100 and the bails 72 preferably are arranged at
the sides and the legs 285 are arranged at right angles
thereto at the front and back.
Figures 8A and 11A to 11F show a pair of connection
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lock members 340. Corresponding connection lock member
pairs (like the members 340) have corresponding teeth 341
that mesh to lock together: the quill 50 and the mud
saver apparatus 90; and the mud saver apparatus 90 and
the saver sub 290. Keys 395 on the quill 50, keys 395a
on the mud saver apparatus 90, and keys 395b on the saver
sub 290 are received and held in corresponding keyways
344 of the connection lock members 340 (keys labelled "K"
in Figure 11F). The connection lock members 340 are
secured with set screws 402 extending through holes 342.
Clamps 401 clamp around the quill 50, the mud saver
apparatus 90, and the saver sub 290 (see Figure 8A and
Figures 11E, 11F) to maintain the connection lock members
in position with keys in their respective keyways. Use
of the connection lock members 340 provides a positive
releasable lock of the quill 50 to the mud saver
apparatus 90 and of the mud saver apparatus 90 to the
saver sub 290 so that the top drive cannot unscrew the
mud saver apparatus 90 from the quill 50 or the mud saver
apparatus 90 from the saver sub 290. Thus joints can be
made and broken with the system 10 without the mud saver
apparatus 90 separating from the saver sub and without
the quill 50 separating from the mud saver apparatus 90.
Optionally, a connection apparatus apparatus 18 (see
Figures 23A - 23G is used instead of a becket 16 as in
Figure IA and a travelling block/hook combination, for
example as in Figure 2G) used in the apparatus 10 which,
in one particular embodiment, adds only 43cm (17 inches)
to the apparatus's height and which eliminates the need
for a standard block/hook combination which can be over
2.7m (9' high). Pin holes 303a in a becket 303 are
alignable with pin holes 420a (four of them equally
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spaced apart in the block 420) in a block 420 to permit
selective positioning of the becket 303 with respect to
the block 420. This allows selective orientation which
can, for example be beneficial in some smaller rigs with
crown sheaves oriented differently from those in other
rigs. The connection apparatus 18 comprises a plurality
of sheaves 420. It is within the scope of the present
invention to use any desired number of becket and block
pin holes to provide any desired number of positions.
The becket 303 has ears 305, 307 with holes 305a, 307a
respectively through which extend pins 309 to releasably
connect to corresponding structure of the top drive 1.
Plates 311 bolted with bolts 313 to the becket 303
releasably hold the pins 309 in place. A shaft 422 of
the block 420 is received on a channel 315 of the becket
303. Plates 424 bolted to the shaft 422 with bolts 426
and bolted to a bushing or retainer 428 with bolts 432
retain the becket 303 on the shaft 422. The channel 315
and the shaft 422 may be threaded for threaded connection
of the block 420 and the becket 303. Typical lines or
cables (not shown) are disposed around sheaves 434 which
rotate around a shaft 436 of the block 420. The
connection apparatus 18 can be lifted and lowered using
the eyes 442.
In one particular aspect, the height of a system 10
with a connection apparatus 18 is about 5.8m (19') from
the becket throat down to a tool joint in an elevator
using upper links which are about 2.4m (96") long and a
hook is used which may be, for example 3m (10') long.
Using an integrated connection apparatus becket system in
accordance with the present invention this overall height
is about 6.25m (20'6").
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Using the hollowbore permanent magnet motor 30,
planetary gear system 20 and a standard swivel packing
assembly mounted on top of the motor 30, a fluid course
is provided through the entire top drive from the
gooseneck 46 down to the saver sub 290 and then to a
tubular or tubular stand connected to the saver sub 290.
In certain aspects, this fluid course is rated at 345
bars (5000 psi) working pressure (for example a fluid
course of about 3" in diameter from the wash pipe down to
the saver sub). The swivel packing assembly (see Figures
16A, 16B) includes a standard wash pipe assembly 370 with
a wash pipe 374, unitized packing 381, 385 and union-type
nuts 371, 372 which allow the assembly to be removed as a
unit.
Figures 12A to 12C illustrate an optional crossover
sub 350 with a body 351 which has interior threads 352
for selective releasable connection of the sub 350 to the
lower end of the quill 50. Upper teeth 353 mesh with
corresponding teeth of a connection lock member on the
quill 50. Lower teeth 354 can mesh with teeth of a
connection lock member on the mud saver apparatus 90
located below a quill 50. These mesh teeth prevent
unwanted disconnection. A smaller diameter threaded end
355 can threadedly mate with a correspondingly-threaded
mud saver apparatus.
Figure 13 shows the bonnet 44 with its lower housing
361 which houses the brake system 40 and with an upper
plate 362 with a hole 362a for the gooseneck 46. Hatches
363 provide access to the brake apparatuses 180 and
permit their removal from within the bonnet 44.
A load nut 366 is shown in Figures 14A and 14B. As
shown in Figure IF, the load nut 366 holds the load
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collar 70 on the load sleeve 170. The load collar 70
rotates on a bearing 367 housed within a recess 368 of
the load nut 366. Threads 369 mate with threads 170e on
the load sleeve 170 to secure the load nut 366 to the
load sleeve 170.
The rotating head 80 shown in Figure 1C and Figures
15A to 15H at the bottom of the load sleeve 170 has an
inner barrel 230 with a body 82 with an upper flange 83
and an outer barrel 372 with rotating ears 373 which are
received in recesses 374 (see Figure 8D) in the outer
legs 285 of the clamping apparatus 100 to insure that the
rotating head 80 rotates with the clamping apparatus 100.
A recess 84 in the inner barrel 230 provides space for a
stabilizing bearing 85 which stabilizes the bottom end of
the quill 50. A bearing retainer 560 retains the bearing
85 in place. Bolts 561 (eight; one shown) bolt the inner
barrel 230 to the load sleeve 170. A gap 562 (for
example between 0.75cm (0.30 inches) and 0.25cm (0.10
inches)) between the inner barrel 230 and the load nut
366 prevents a load from being transmitted from the load
nut to the inner barrel. Bolts 563 prevent the load nut
366 from rotating.
The inner barrel 230 has three ports and (channels)
230a and lubricating channel port 230a-1 which
correspond to and are aligned with the four channels 170a
of the load sleeve 170 and fluid flows down through the
channels 170a into the ports 230a - 230d. Three of the
channels 230a are in fluid communication with
corresponding paths 372a, 372b, 372c of the outer barrel
372 and one of the channels 230a-1, a lubrication channel
provides lubrication to items below the rotating head 80
(for example the lower quill stabilizing bearing 85).
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Four seals 372s isolate the paths 372a-c.
The location and function of the rotating head 80
(which rotates with items like the clamping apparatus 100
below the top drive gear and motor components which are
rotated by the motors 190) makes it possible to have a
lower hydraulic manifold 400 with flow-controlling
directional valves which also rotates when the motors 190
rotate the clamping apparatus 100. By locating the
generator 240 at this level, electrical power is provided
for the directional valves by the generator 240.
Figures 16A and 16B illustrate the wash pipe
assembly 370 which is located at the top of the quill 50
within the bonnet 44. In use the nut 372 does not rotate
and is remains stationary with the goose neck 46 which is
connected thereto so that fluid is flowable through the
gooseneck 46 into a central fluid channel of the nut 372.
The nut 371 has a female threaded end for threaded
connection to the top of the quill 50. The nut 371
rotates with the quill 50 about the wash pipe 374.
Figures 17A to 17H show the access platform 130 of
the top drive 1 (see, for example also Figures 1A, 1B,
1D). Upon release, the access platform 130 is pivotable
from a position as shown in Figure 17G to a position as
shown in Figure 17H, supported by one or more cables 134.
In the position of Figure 17H, a person can stand on the
access platform 130 to access the motor 30, and/or items
connected to an inner guard member 135 (shown in Figures
17H, 171), for example items including items on a rear
guard 454 including a heat exchanger 455, pump 458, upper
electric junction box 450, extend accumulators 451,
filter 457 for hydraulic fluid, motor 459, pump 458, flow
meter 456, upper hydraulic manifold 452 with electrically
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powered directional valves 453 (one or which is a shut
off valve for shutting off pressurized fluid flow to the
rotary seal which is activated upon rotation of the pipe
handler so that the rotary seal is not damaged by
pressurized fluid). Connectors 136 are bolted to the
swivel body 12 and a stabilizer member 137 is connected
to a motor flange 30f. Connectors 130a of the access
platform 130 are hingedly connected to connectors 136a of
the rear guard 454, for example with a pin or pins 130c.
Bolts 130b through holes 130d releasably secure the
access platform 130 to the top of the rear guard 454. An
optional brace 138 extends across the interior of the
access platform 130. Optionally, bevelled, tapered,
rounded, or chamfered edges 139a, 139b, 139c, 139d, 139e
are used and/or with a tapered bottom portion 139d to
inhibit items catching onto part of the access platform
130. The access platform 130 can be lifted using an eye
member 130e.
Figures 18A and 18B illustrate a motor dam 31
emplaced on the motor 30 to inhibit drilling mud or other
fluid from getting into the motor 30.
Two slingers, slingers 76 and 77, inhibit fluid (for
example drilling mud) from contacting the brake system
40, Figures 19A and 19B show an upper slinger 76 with a
recess 76b for accommodating a lip of the bonnet 44 and a
groove 76c for an O-ring seal to seal the slinger/quill
interface. Figures 20A and 20B show a lower slinger 77
with an O-ring groove 77a for an O-ring seal to seal the
slinger/quill interface. These slingers prevent drilling
fluid from getting on the brake disc.
Figures 21 and 22 show a wear sleeve locking guide
62. This wear sleeve lock guide acts as a bearing on
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which the rotate gear 193 rotates and also maintains a
desired gap between the rotate gear 193 and the lock
guide 62. In one aspect the guide 62 is made of phenolic
material.
Figures 24A, 24B, and 25 show the spacer plate 22
with its recess 22a for receiving the bearing 59. The
gear system 20 sits in a recess 22b. An extension 22c
fits into the channel 12c in the swivel body 12. Through
a hole 22d passes lubricating fluid coming from the gear
system 20 which flows down into the swivel body 12 and
then downward to lubricate items below the swivel body
12. From the swivel body 12 this lubricating fluid flows
into the lubricating path of the load sleeve 170 and from
there to the rotary seal 80, then to the lower stabilizer
bearing 85. A shoulder 22s inhibits bearing deflection,
for example while jarring, and makes it unnecessary to
re-set bearing pre-load.
Figures 26A to 26E show arms 430 which is for
facilitating movement of the bails 72. Each arm 430 has
a body member 432 with an upper connector 434 at the top
and a lower connector 435. A slot 436 extends through
the body member 432.
A lower portion 437 of the arm 430 is disposed
outwardly (for example to the right in Figure 26C) from
the arm's upper part. A hole 438 permits connection to
the link. Holes 439 permit connection to the load
collar. This disposition of the lower portion 437
facilitates movement of the link with respect to system
components adjacent this portion of the link.
Figures 27A to 27F illustrate how clamp 126 of the
movable bale apparatus (link tilt system) 120 can
accommodate bails of different cross-sectional diameters.
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The clamps 126 have two roller pins 127a, 127b each with
a roller 127d and roller mounts 127c. Holes 127e are
offset in each roller mount 127c providing two positions
for the rollers 127d. As shown in Figures 27A and 27D, a
bail A (like the bail 72) moves between the rollers 127d
and is, for example about 7.3cm (2 7/811) wide. As shown
in Figures 27B and 27E, with the rollers 127d in the same
position as the rollers 127d in Figure 27D, a bail B
(like the bail 72) is accommodated, for example a bail B
with a width of 8.9cm (3.5"). As shown in Figures 27C
and 27F, the roller mounts 127c have been repositioned in
holes 127f, moving the rollers 127d further apart so that
the clamp can accommodate a wider link, for example the
link C (like the link 72) which is 4.5" wide. A grease
nipple 127g is provided for each pin 127a, 127b. Each
pin 127a, 127b has a threaded end (a top end as viewed in
Figure 27D) which is threadedly engaged in corresponding
threads in the roller mounts 127c (top roller mounts 127c
as viewed in Figures 27D, 27E, 27F). Holes in the other
roller mounts (lower ones as viewed in Figures 27D, 27E,
27F) may be unthreaded. In one aspect, bails A are 250
ton bails; bails B are 350 ton bails; and bails C are 500
ton bails.
Figure 3 (3A to 3E) show schematically a control
system 150 with an hydraulic circuit 150a and a coolant
circuit 150b (Figure 3F) for the a top drive 152 (such as
any top drive disclosed herein) with a building 160
adjacent a location of the top drive 152. The building
160 houses various circuits and controls, among other
things, as discussed in detail below. For parts of the
apparatus disclosed herein using hydraulic fluid, either
a hydraulic fluid may be used or a water/glycol mixture
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may be used.
Figures 28A to 28C and 28E show the building 160 on
a skid 540 in accordance with the present invention which
has four walls 161a to 161d, a floor 161e, and a roof
161f (which in one aspect comprise a typical ISO
container). A carrier 169 (see Figure 28E) with a skid
169a with fork lift pockets 169b is mounted on top of the
roof 161f for holding and storing of the service loop
and/or of hoses. Doors 541 are at both ends of the
building 160 and doors 541a and 541b (optionally vented
with vents 541f) are on a side. Windows 541c are on a
side and vent openings 541d, 541e are on another side.
Pieces 82b of the beam 82 or ("torque track") are housed
within compartments 162 in the wall 161d. A space 163
within the building 160 is sufficiently large to hold the
major components of an apparatus like the apparatus 10
shown in Figure 1A. In certain aspects, the building 160
contains a 600 volt panel PL for running motor starters,
Variable Frequency Drive (VFD) controls, transformers
(for example 100 kva and 10 kva) , and fuses for all 600
volt equipment. There is a 120 volt panel PN and a 24
volt panel PE that supplies 24 volt control power for the
drive system for a pre-charge circuit; and a battery
back-up BB to maintain control power alive when rig power
is lost to control various items, for example, flow
meters, flow switches, tank heater, unwind, lights,
circulating engine heater and/or A/C, building heaters
and/or A/C, temperature transducers, emergency shut down
apparatus (ESD), fuses and motor control starter
circuits. Panels PL, PN, PE, emergency shut down
apparatus ESD, and battery back-up BB are shown
schematically in Figure 28E.
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The building 160 also houses electrical power
generator 530 (for example diesel powered); variable
frequency drive system 531 for providing electrical power
for the motor 30; a temperature /humidity control system
531a for controlling temperature and humidity of the
system 531 and of a coolant system 532; an hydraulic
fluid tank 533; an electrical junction box 534; an
optional control system 535; pumps 536 and radiators 537
of the coolant system 532; and furniture and furnishings,
for example item 538. An optional vacuum system 688 will
remove drilling fluid from the system in the event of a
shut-down so the fluid will not freeze in the lines. The
coolant system (see Figure 3A) 532 provides cooling
fluid via the service loop 48 to the gear system 20 of
the top drive 152 and to the swivel body 12. A motor
150c drives a pump 150d which pumps cooling fluid through
a filter 150e and a heat exchanger 150f. Whenever the
pump 150d is on, the gear box 150g of the gear system 20
is provided with full lubrication at whatever speed, for
example 1 rpm or full speed. Cooling fluid (lubricating
oil) flows from a top bearing 150h to the gear box 150g.
In certain aspects the beam 82 serves as a "torque
tube" through which torque generated by the top drive is
reacted from the top drive, to the extension mechanism
98, to the beam 82 and then to the derrick. In one
particular aspect part 82a of this beam 82 is used as a
skid or support on which the top drive is mounted to
facilitate transport of the top drive; and this part 82a
of the beam 82, with a skid portion 82d, is removably
housed in the building 160 with the top drive in place
thereon. In one particular aspect (see Figure 2F), a top
piece 82f (Figure 2D) of the beam 82 is length adjustable
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to accommodate different derrick conditions. In one
aspect one, some or all of the pieces are length
adjustable, for example two telescoping pieces 82g, 82h
which can be pinned through one hole 82j and one hole 82k
with a pin (or pins) 82i at a number of different lengths
depending on the holes selected; and/or such pieces can
be threadedly connected together with threads 82m, 82n
for length adjustability. Pieces that make up the beam
82 may have holes or pockets 82e for receiving a fork of
a fork lift.
In one aspect as shown in Figures 31A to 31H, the
top drive is mounted on a skid 620 which is removably
emplaceable within a mount 622 of a reaction frame 600.
The skid 620 (like the skid 82d, Figure 2A) and reaction
frame 600 once installed, with the skid 620 connected to
the beam 82, remain in position while the top drive is
movable up and down on the beam 82. In one aspect the
reaction frame 600 is welded to the skid 620. Torque
generated by the top drive is reacted through the skid
620, through the reaction frame 600, into and through the
beam 82, and then into the derrick 140 (and into other
structure connected to the derrick and/or into
substructure or derrick substructure). Thus reacted
torque is passed through the skid rather than to the
derrick structure alone.
The reaction frame 600 has a rear beam 606 with a
lifting eye 608. Side beams 602 move within holders 610,
612 on the rear beam 606. Clamps 604 releasably clamp
the reaction frame 600 to the beam 82. Clamps 605
adjustably clamp the side beams 602 to the rear beam 606.
Piece 614 is a piece of a torque track welded to the skid
620. The side beams 602 extend into and are held within
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corresponding holes 624 in the mount 622. The skid 620
with the top drive 1 is located on the mount 622. The
skid 620 with the top drive 1 connected to it is held by
and is movable vertically with respect to slide members
623 (see, for example Figure 31E). Thus the skid 620 and
top drive can mate vertically with respect to the
reaction frame 600 to isolate the reaction frame 600 (and
the derrick) from vertical loads. The skid 620 and
reaction frame can be sized and configured so that the
skid 620 with the top drive 1 can move any desired
vertical distance with respect to the reaction frame, for
example, but not limited to, from 2cm to 215cm (one to
sixty inches) , and in one particular aspect, movable
vertically about 1.3cm (one-half inch).
Figures 31A and 31B illustrate the range of motion
of the reaction frame 600 (with the top drive attached
thereto) toward and away from a well centre. A transport
stand/support 630, Figure 31D encloses a top drive for
shipping on the skid 620 and pins 630a are pinned into
corresponding holes on a beam 82. The stand/support
secures the top drive for shipping.
As shown in Figures 2C to 2D, an opening 375 between
members of the extension mechanism 98 provides a
passageway through which can pass a tubular stand 376
once a top drive 1 supported by the extension mechanism
98 is extended so that the top drive is no longer over
the stand. This can be beneficial in a variety of
circumstances, for example, when pipe is stuck in the
well or the top drive needs to be accessed, for example
for inspection or repair. The saver sub is disconnected
from the stand; the top drive is moved further outwardly
so it is no longer directly over the stand; and the
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extension mechanism 98 is lowered with the stand moving
through the opening 375. This permits access to the top
drive at a lower level, for example at or near the rig
floor. The source of power for the cylinder assemblies
392 of the system 98 is the accumulators 451 (see Figure
17D). The assemblies 392 are pivotably connected to
support structure 393 with top drive mount 394 which is
secured with bolts to the swivel body 12.
Control of the various components of the apparatus
is provided by a control system that includes: the
driller's panel 141; a digital signal processor ("DSP")
system 256a in the driller's panel 141; a DSP system 256b
in the upper electrical junction box 450; a DSP system
256c in the lower electrical junction box 250; and/or a
DSP system 256d with the control system 531. Each DSP
system has an RF antenna so that all DSP systems can
communicate with each other. Thus a driller at the
driller's panel 141 and/or a person at the control system
531 can control all the functions of the apparatus 10.
Lubrication oil (hydraulic fluid) flows in the
service loop 48 (see also Figure 3F) to the plugboard
391; into the upper hydraulic manifold 452 and heat
exchanger on the rear guard 454, behind the access
platform 130; through the filter 457 with flow metered by
the flow meter 456; out to the gear system 20 (cleaned by
the magnetic plugs 494) with level indicated in the sight
glass 481; out the bottom of the gear system 20, lubing
the splined portion 52 of the quill 50 and the upper
bearing 59; into the swivel body 12 and out its drain
12s; into the load sleeve lubrication port and down a
channel 170a of the load sleeve; into and through the
rotating head 80 through the lubrication port of the
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inner barrel 230; to the lower quill stabilizing bearing
84; up through a space 405 between the load sleeve 170
and the quill 50 through the self cleaning main bearing
56; then back to an out line in the plugboard 391 and
into an exit line in the service loop 48. Optionally, an
oil lube pump OLP for the system's lubricating system may
be located in the guard 73 for pumping lubricating fluid
to the various parts of the system that are lubricated.
Hydraulic fluid flows through the other three ports
(other than the lube port/channels) in a similar fashion.
Appropriate lines, hoses, cables, and conduits from the
service loop 48 (including electrical lines etc. to the
upper electrical junction box 450) are connected to the
plugboard 391 and from it: control cables to the upper
electrical junction box 450 and to an upper junction box
(not shown) of the motor 30; hydraulic lines to the upper
hydraulic manifold 452 and to the lubrication system;
coolant fluid lines to the motor 459 and heat exchanger
455. Power cables from the service loop 48 are connected
to the junction box of the motor 30.
Cables from the service loop 48 are connected to
corresponding inlets on the plugboard 391; for example,
in one aspect, three hydraulic fluid power lines are used
between the plug board 391 and the upper hydraulic
manifold 452 - an "in" fluid line, and "out" fluid line,
and a spare line for use if there is a problem with
either of the other two lines. Also in one aspect there
are three lines from the plug board 391 to the motor 459.
The motor 459 powered by hydraulic fluid under pressure,
drives a pump 458 which pumps fluid to items below the
rear guard 454. The fluid that is provided to the pump
458 is a coolant fluid (for example glycol and/or water;
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ethylene glycol) provided in one of the lines of the
service loop 48. The pump 458 pumps the coolant fluid to
and through the heat exchanger 455 and then, from the
heat exchanger 455, the fluid is pumped to items below
the access platform 130 for lubrication and for cooling.
The fluid that flows through the motor 459 returns in a
line back to the service loop 48 (for example back to a
fluid reservoir, for example the fluid reservoir 533,
Figure 28D). Optionally, the fluid from the motor 459
can first go through the heat exchanger 455 then to the
service loop 48. Appropriate lines with flow controlled
by the directional control valves 260 provide hydraulic
power fluid to each of the items powered thereby.
Figures 32A to 32E illustrate various embodiments of
top pieces of a torque track for use with top drives as
disclosed herein. (The beam 82, Figure IA, can be
referred to as "guide Beam" or "torque track".) A top
piece 630 of such a torque track has a body 632 within
which is connected a receiver 634 having a plurality of
connection holes 636. One end of safety cables can be
attached to shackles 638 with the other end attached to
any suitable structure, for example part of a derrick,
for example part of the crown of a derrick. Any suitable
number of torque track pieces are used at a given
installation to adjust the distance of the torque track
skid with respect to a rig floor. Moving a member 640 in
and with respect to the receiver 634 provides
adjustability of the height of the torque track in its
entirety with respect to the derrick 140 and the rig
floor. A system 696, like the items in Figures 32A to
32E, shown in Figure 2A may be used to suspend the
apparatus in a derrick and to provide height
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adjustability for the apparatus. One or more pins 642 is
used to releasably connect the member 640 to the receiver
634. Optionally, two shackles 644, 646 are used to
connect member 640 and the top piece 630 (and thus the
entire torque track) to the derrick 140. Such a free
two-shackle connection prevents torque from being
transferred to the derrick 140 through the top piece 630,
preventing such torque from being reacted through the
torque track to the derrick, particularly to and through
the top of the derrick. Apparatuss in accordance with
the present invention have a "pull down" capability, i.e.
Weight On Bit (WOB) can be added using cables, winches,
etc. to pull down on the top drive while rotating the top
drive.
Figures 33A - 33C illustrate a structure for sealing
between a brake hub (for example of the brake apparatus
40, Figure 1B) and a quill (as the quill 50, Figure 4B) .
A seal bearing isolator 650 has a body 651 with one, two
or more static O-ring seals 652 in corresponding grooves
652a which seal an isolator/quill interface. Such seals
also seal this interface when the system is non-vertical,
for example during transit. An O-ring 653 seals an
isolator/brake-hub interface. A ring 654 partially in a
recess 654a in a body part 651a and partially in a recess
654b in a body part 651b holds the two body parts 651a,
651b together. A snap ring 655 in a recess 655a in the
body part 651b acts as a slinger slinging oil outwardly.
A felt seal 660 is disposed between the two body parts
651a, 651b and seals the interface of these parts at the
location of the seal 660. Body part 651a moves at the
speed of the quill, for example from 0 to 2400 rpm's.
The body part 651b rotates at the speed of the top drive
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motor, for example 200 rpm's when the quill is rotating
at 200 rpm's. The body part 651 sits in the brake hub
held therein with a friction fit (for example as shown in
Figure 4B). The felt seal 660 is grease or oil filled.
When the seal is rotated (for example when the quill is
rotated), the seal has forces on it tending to move
grease or oil out of the seal.
Figures 34A and 34B illustrate an embodiment of a
seal system 661 in accordance with the present invention
for sealing between a gear system and a motor of a
apparatus. The seal system 660 has a lift seal 662 which
seals against a surface of a rotating sun gear 680 of a
gear system 690 (for example, but not limited to, a sun
gear as in any gearing system described above). The lift
seal 662 includes a mechanical seal 664 bolted with a
bolt 665 to a part 667 of a piston rod 668. The piston
rod 668 is movable with respect to a non-rotating seal
housing 670 (top plate of gear box). A spring 672 urges
the piston rod 668 upwardly, thus urging the seal 664
against the sun gear 680. The piston rod 668 moves in a
piston cylinder 677 which has a lower side 676. A seal
674 seals the rod/cylinder interface. Seals 671a seal
the cylinder/seal housing interface. A lock member 677b
holds the cylinder 677 in place (or it may be bolted in
place). A bottom flange 678 of the motor is on top of
the seal housing 670.
The pathway that is sealed by the seal 664 is a
pathway through which oil from the gear system can flow
from the gear system to a motor 692 of the top drive.
When the top drive is operational oil flowing into an oil
supply port 679 from an oil supply and through a channel
681 into a cylinder housing 677a pushes down on the
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piston rod 668 and the seal 664 is disengaged from the
sun gear 680. When the apparatus is off (oil is not
flowing through the channel 681) the spring 672 urges the
piston rod 668 upwardly so that the seal 664 engages the
sun gear 680, thus closing off the oil flow path and
preventing oil from leaking from the gear system into the
motor (for example, in one aspect, if the apparatus is in
a non-vertical orientation). A brake hub is secured to a
top 692a of the motor's rotor.
Figures 35A to 35F illustrate a length adjustable
link 700 useful as a support link for supporting any item
or equipment and which, in certain aspects, is useful as
any of the links described above, for example bails 72 or
links 14. Each link 700 has a hollow first part 701 in
which is movably disposed a portion of a second part 702.
The first part 701 has an eye 703 and the second part 702
has an eye 704. Bolts 705 through holes 706 in the first
part 701 and through holes 707 (or holes 708) in the
second part 702 releasably secure the parts 701, 702
together. Any desired number of holes at any desired
location may be provided in the first part 701 and/or in
the second part 702 for link length adjustability. The
resulting length of the link as shown in Figures 35C and
35F. As shown the link parts (outer and inner) have a
generally square or rectangular cross-section, but this
cross-section may be any desired shape, for example, but
not limited to, circular, oval, elliptical, triangular,
pentagonal, or hexagonal. The rear views of the links as
shown in Figures 35B, 35C, 35E and 35F are like the views
of Figures 35B, 35C, 35E and 35F, respectively. The side
view opposite the side shown in Figure 35A is like the
view of Figure 35A.
