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Патент USA US3033539

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May 8, 1962
Original Filed Oct. 24, 1957
5 Sheets-Sheet l
May 8, 1962
Original Filed Oct. 24, 1957
5 Sheets-Sheet 2
F7 2
May 8, 1962
Original Filed Oct. 24, 1957
5 Sheets-Sheet 3
May 8, 1962
Original Filed Oct. 24, 1957
5 Sheets-Sheet 4
May 8, 1962
Original Filed Oct. 24, 1957
5 Sheets-Sheet 5
United States Patent O?tice
Patented May 8, 1962
~ FIG. 2 is a vertical sectional view taken on the line 2—2
of FIG. 1, looking in the direction indicated by the
FIG. 3 is a sectional view taken on the line 3-—3 of
.lohn Hart Wilson, R0. Box 1031, Wichita Falls, Tex.
5 FIG. 2, looking in the direction indicated by the arrows;
Continuation of application Ser. No. 692,130, Oct. 24,
and showing the drive and braking mechanism of the feed
1957. This application May 22, 1961, Ser. No. 116,911
5 Claims. 7 ((11. 254-173)
control unit;
FIG. 4 is a diagrammatic view of the air control system
of the feed control device;
This application is a continuation application of Serial
Number 692,130, ?led October 24, 1957, now abandoned. 10 PEG. 5 is a diagrammatic view of the hydraulic system
used in connection with the feed control device; and
This invention relates to a feed control device for
FIG. 6 is a diagrammatic, elevational view of a typical
drilling rig hoist drums, such as used on rotary drilling
derrick construction, showing blocks, a Kelly’ joint, and
drill stem as used in a drilling operation in a well. '
Heretofore, the “feed-oil” of a drilling line from a
With more detailed reference to the drawing, the nu
hoist of a drilling rig was normally left to the judgment 15
meral l. designates generally the draw works of a drilling
of the individual driller, and if the driller was impatient,
rig, which unit has sills or frame 2, and a hoisting drum
or the line was fed off too fast, the result frequently was
4, which hoisting drum is mounted on a shaft for rota
the sticking of the drilling bit, with the drill stem fre
tion of the drum 4- about its axis. It is the usual prac
quently being twisted in two, however, an overcautious
driller, who hesitated to let the drill line off as rapidly 20 tice to have a high speed clutch 8 connected to the drum
shaft d at one end of the drum in driving relation there
as the bit could drill the formation, could materially re
with, and a low speed clutch 10 connected to the drum
tard the drilling operation.
shaft 6 at the other end of the drum 4 in driving relation
The present invention is designed to keep a prede
therewith. An over-running clutch 12 is provided within
termined amount of weight on the drill bit, and if the
formation being drilled cuts easily, the drilling line will 25 the drive system, intermediate the high speed. clutch 8
feed off as rapidly as the bit will drill the formation, but,
if the progress of the drilling is retarded, due to hard for
mation, the drilling line will not be fed off the drum with
su?icient rapidity to cause the bit to become stuck.
Various attempts have been made heretofore to con— 30
and the hydromatic brake 14. The clutches 8 and 10 are
of the pneumatic type and. are supplied with air through
conduits 16 and 18, respectively, which conduits lead
through a rotary fluid seal 20, in a manner well under
stood in the art.
Conduits (not shown) convey the pneumatic pressure
from the rotary seal 20, on the outer end of shaft 32 of
the hydromatic brake 14, to‘ the respective clutches 8
‘and 10, through hollow shafts and other conduits, as is
The present device is so constructed, that once it is 35 well understood in the art of Pneumatics.
The drum 4 is usually driven'by roller drive chains
set to operate under predetermined conditions, it requires
little or no attention, so long as the drilling operation is
22 and 24, which pass around sprockets 26 and 28, re
spectively, which sprockets are journaled on drum shaft
progressing in a uniform manner.
An object of this invention is to provide a feed control
6, and around complementary sprockets (not shown) on
device for the hoisting drums of drilling rigs, which device
counter shafts, transmissions or the like, to drive the
is sensitive to the change in weight of the string of drill
drum in a manner well understood in the art of drilling.
stem, and which will feed cable off the hoisting drum at
A sprocket Si} is mounted on shaft 32 which shaft 32 is
a rate commensurate with the change in weight on the
in axially aligned relation with drum shaft 6. A chain
34- surrounds sprocket 36* and sprocket 36, on feed con
drilling bit.
Another object of the invention is to provide a feed
trol shaft 38.~ The feed control shaft 33 is mounted with
control device for the drum of a rotary drilling rig,
in the feed control device which is designated generally by
whereby the drilling line will be fed off in accordance
the numeral 4%‘. The shaft 38 has asprocket 42 journaled
with the weight being maintained on the drill bit and
thereon for turning movement about the shaft. The
which will limit the rate of “feed-off” of the drilling line,
sprocket 42 has clutch jaw teeth 44 thereon, which teeth
in event the drill bit should suddenly drop into a cavity
extend outward therefrom. A sliding clutch 46 is splined
trol the “feed-off” of line from drums, however, these
devices for the most part, were too complex and bulky
and required such excessive maintenance as to make
their use impractical in oil ?eld drilling.
or drill into a soft, mushy formation.
Still another object of the invention is to provide a
sprocket 42, when in one position, and to disengage the
feed control device for drilling rig drums which will auto—
jaws 44, when in another position.
matically release, when taking up the empty blocks, there
by minimizing wear on the feed control unit.
Yet another object of the invention is to provide a feed
control unit for drilling rig drums which has a minimum
of working parts, yet which is sensitive to small changes
in the load so that uniform weight can be maintained on
to shaft 38 so as to complementally engage jaws 44 on
A drive chain Stl passes around sprocket 42 and around
sprocket 52, so as to connect shaft 38 in driving relation
with shaft 54. The sprocket 52 is secured to shaft 54
and upon rotation of shaft 54, sprockets 52 and 56, the
sprocket 56 also being secured to shaft 54, will be ro
tated therewith.
On the opposite end of shaft 54 from the sprocket 56,
the drill bit at all times.
A still further object of the invention is to provide a
is an air actuated brake, which is generally designated by
feed control device for drilling rig drums which is simple
the numeral 58, as will best be seen in FIGS. 2 and 3.
in construction, low in cost, ‘easy and effective in opera
The brake 58 is controlled by air pressure which is ap
tion, and which requires a minimum of maintenance.
plied through conduit 122 from a remote point, as will be
With these objects in mind and others which will be 65 explained in detail hereinafter.
come manifest as the description proceeds, reference is
The air actuated brake 58 has a toothed hub 62 there
to be had to the accompanying drawings, in which like
in, which toothed hub is mounted on and secured to the
reference characters designate like parts in the several
shaft 54. The toothed hub 62 engages the inner teeth of
views therein, in which:
FIG. 1 is a fragmentary, top plan view of a drilling 70 plates 64 within brake 58. A plurality of friction disc
elements 66 are provided, which elements have peripheral
rig hoisting drum, showing the feed control device at
which teeth engage complementary teeth 68 around
tached thereto;
the inner diameter of cylindrical shell 70 of the brake
element 58.
An annular disc 72 is positioned against the outermost
of the friction elements 66, which annular disc is made of
a heat resistant material, such as molded asbestos or the
like, and is ribbed to minimize the transfer of heat and
to permit air to circulate therethrough. An elastomer
pressure tube 74, which is axially expansible, is positioned
within the cylindrical casing 71} of the brake element 58,
and is in abutting relation with end member 76, which 10
end member 76 is secured to cylindrical casing 713 by
A gauge protector valve 128 is provided in the ?uid
loaded pipe 146, intermediate the sensator diaphragm
member 132 and the inverse relay 126. The purpose of
the valve is to reduce or cut off excessive pressure gen
erated by the sensator diaphragm member from the in
verse pressure relay 120. The valve 128 is of the type
which is commonly used as gauge protectors to prevent
damage to the sensitive members in gauges and instru
ments such as diaphragms, within the inverse pressure
relay 120.
A pressure gauge 124i is positioned within pipe 122 to
means of cap screws 78. The other end of the cylindrical
determine the correct pressure to be maintained on pipe
casing 70 is closed by an end member 86, which is so
122, and on expansible tube 74. The ?uid loaded pipe
cured thereto by means of cap screws 32. The end
146 leads from inverse pressure relay 12% through the
member 89 is also secured to the stationary gear reduc 15 pressure protector valve 12%, valve 144 and through T
tion housing 84 by means of cap screws 36, which hous
139 to sensator diaphragm member 132 connected to ?uid
ing is rigidly secured to frame 2.
loaded pipe 146. The pipe 146 is preferably ?lled with
With the friction elements 66 ‘being connected to the
low expansion, low freezing liquid, so it will react accurate
cylindrical casing 79 and to the gear reduction housing
ly to the inverse relay 1211, upon movement of the sensa
84 through teeth 68, and with the plates 64 connected to 20 tor diaphragm member 132.
shaft 54 through toothed hub 62, it will be seen that,
The sensator diaphragm member 132 is pivotally con
upon application of pressure by axially expansible tube 74,
nected, at one side, to an arm 134 and to a lever 136 on
the plates 64 and 66 will be brought into frictional engage
the opposite side. A winding drum 138 has several turns
ment, and that the frictional engagement will be propor
of cable 142 thereon, one end of which cable is indicated
tionate to the amount of pressure which is applied to the 25 at 142 and extends upward into the derrick and over the
tube 74 through air conduit 122. The shafts 38 and 54
crown block sheaves, to form a “dead line.” The other
are journaled on bearings 39 in gear housing 84, and on
end 142a of the cable 142 is anchored to lever 136, so
bearings 45 therein, to make possible the free rotation of
as to impart movement to the lever 136, which movement
these shafts, respectively.
will be proportionate to the amount of pull that is being
A sprocket and chain housing 88 is mounted adjacent 30 imparted to the‘ cable. The sensator diaphragm member
housing 84, and is rigidly connected therewith and ex
132 is connected intermediate lever 136 and arm 134, so»
tends thereabove. A hydraulic pump 90 is mounted near
as to react to the pull on cable 142. The pipe 146 leads
the upper end of housing 88 and has a sprocket 92 there
from sensator diaphragm member 132 and connects to
on, which sprocket 92 on pump shaft 93 is in aligned,
the inverse pressure relay 120‘ and to a pipe 148 leading
driving relation with the sprocket 56 on shaft 54. A 35 to a weight indicator 15%‘. The sensator diaphragm rnem~
chain 94 passes around sprockets 5.6 and 92, so as to
her 132 is sensitive to pull applied to the cable and trans
couple the pump 90 in driven relation with the shafts 54
mits pressure to the weight indicator and to the inverse
and 38..
pressure relay 120 proportionate to the pull. A valve
The hydraulic pump 90 has an intake pipe 96 extending
144 is provided within pipe 146 to enable the closing of
into hydraulic ?uid reservoir 98. A ?lter screen 100 is 40 the conduit between inverse pressure relay 1% and the
shown in the intake pipe 96, just inside the reservoir 98,
and a discharge pipe 1&2 leads from the hydraulic pump
diaphragm 132, which renders the brake 58 inoperative,
yet permits the weight indicator to function in the same
90 to a pressure relief valve 104, with another discharge
manner as if the feed control unit was not connected there
pipe 106 leading from pipe 162 through metering valve
to. A pipe 148 leads from the other end of T 131), and
108, which metering valve 103 may be of the manually 45 extends to weight indicator 150 which is connected within
operated globe or needle type, or it may be of the re
?uid loaded pipe system 146—148.
mote controlled type, so that the discharge of ?uid there
through, from the hydraulic pump 90, may be accurately
adjusted. A by-pass 1110 leads from the relief valve 104
In the drilling of deep wells, such as oil wells and the
into discharge pipe 1117 at a point between the metering 50 like, various earth formations are encountered, some of
valve 108 and the discharge outlet 112 in the reservoir 93.
which drill easily, and in some of which drilling is very
The pressure relief valve 104 in pipe 1% is set to dis
di?icult, and frequently crevices, caverns, and the like
charge into pipe 110 at a given pressure, however, if the
are encountered, into which the drill stem will suddenly
restriction in the metering valve 108, in pipe 196, causes
drop, if not retarded. The rotary table will rotate the
the pressure to exceed the predetermined setting, the ex 55 drill stem with the drill stem furnishing the weight, where
cess pressure ?uid will be by-passed through by-pass pipe
by the bit will cut into the earth formation. However,
110 into discharge pipe 167 and back into reservoir 98
as more drill stem is added, the weight on the bit becomes
through discharge opening 112. In this manner an ac
curate maximum setting for the speed of the pump can be
excessive, so some of the load is sustained by a block and
tackle arrangement, which is connected between the top
and the derrick D and the rotating swivel joint on the
upper end of the Kelly joint K to which the drill stem
S is connected. The Kelly joint is suspended from the
block B of the block and tackle. The end 142]) of the
cable of the block and tackle arrangement is wound onto
made and accurately controlled, thereby controlling the
maximum speed of rotation of the drum, due to the pres
sure of fluid constrained within the pump, and to the chain
and sprocket drive. This arrangement will prevent a
sudden lowering of the drill pipe, in event an unusually
soft formation, or a cavity in the formation is encountered, 65 a drilling rig hoist drum 4, which drum is provided
as will be more fully brought out hereinafter.
with brakes and is usually provided with a hydrau
_An air supply pipe 114, connected to a suitable source
lic retarder brake, which is usually known as a hydro
of high pressure air,’ not shown, passes through air pres
matic brake. It is the driller’s responsibility, however,
sure regulator valve 116 and which air supply pipe 114
to see that the cable is “fed-cit” the drilling rig hoist drum
has a pressure gauge 118 therein, from which the pres
as fast as possible, consistent with the correct load weight
sure of the incoming regulated air may be determined. 70
on the drilling bit C which extends into the well or bore
W at the lower end of the drill stem S. It is to the end
The air supply line 114 leads to an inverse pressure relay
120, which may be so regulated as to maintain a given
pressure in pipe 122 which leads to the air actuated brake,
which brake is generally designated at 58.
of eliminating the uncertain human element, that the
present device was designed.
Since rotary drilling rigs must frequently be moved
from place to place, it is most desirable to keep all the
accessories and attachments thereto to- a minimum in
weight and bulk, to enable ready transportation thereof,
and while other cable feeding control devices have been
proposed heretofore, these were so bulky, heavy, and
expensive that many operators were reluctant to use such
- devices, furthermore, other weight indicating devices are
insensitive to slight changes in weight and are com iicated
in structure.
, The present device is comparatively light in weight, and
so simple in construction as to be readily attached to the
hoist drum of most rotary drilling rigs, and can be utilized
therewith to maintain even weight on the drill bit, and
of the lever 136 will cause pressure on the diaphragm in
such manner that the liquid reaction in pipes 146 and
148 will act upon the pressure sensitive elements in the
inverse relay 120 and in the pressure sensitive elements
in the weight indicator 150, and with the correct weight
or load on the drill hit, an adjustment knob 121 may he
moved to adjust the elements in inverse relay 120, where
by, as the drill bit drills into the formation and the pres
sure thereon is relieved, which will cause greater weight
on cable 142, which will increase the pressure in pipes
146 and 148, and since the pipe 146 connects with in
verse pressure relay 1211, in a manner well understood in
the art of pressure elements, the increase in pressure on
an element in inverse pressure relay 120 will cause a
which device is sensitive to the slightest change in weight
brought about during the cutting of the bit into the forma 15 proportionate closing of a Valve therein, so air under
pressure will be passed from air pressure supply pipe 114
through regulator valve 116, through inverse pressure
In raising the drill stem out of the hole, it is desirable
relay 120 at a lower pressure into pipe 122. Upon low
to raise it as rapidly as possible, but when it goes into
ering the pressure in pipe 122, which leads to pressure
the hole or well, it is desirable to retard the speed of
the downward movement thereof. In “coming out of the 20 actuated brake 58, the axially expansible air tube 74
will yield to permit relative slippage between the brake
hole” an over-running clutch mechanism 12, which is
plate 64, which engages shaft 54, and the brake friction
connected to the drum 4, it so arranged that, when the
element 66, which is engaged with .cylindrical casing 70.
drum 4 is rotated in one direction, the elements in the
As’ the weight on the cable 142 becomes less, the pres
over-running clutch 12 will not engage, thereby render
sure in the sensator diaphragm member 132 becomes less,
ing the hydraulic retarder 14 immobile. This enables
and since the hydraulic pressure within the pipe system
the hoisting of the drill stem as rapidly as desired with
146-148 will equalize, thereby lessening the pressure
out the hydraulic retarder 14 interfering with the turning
of the drum 4. To return the empty blocks quickly, a
on a pressure sensitive element in inverse pressure relay
126, the valve will be opened, which will permit air
jaw clutch 11 may be utilized, if desired, to disconnect
the over-running clutch unit 12 and the hydraulic re 30 under increased pressure, to pass through pipe 122 into
axially expansible tube 74, so as to retard the feed-off of
tarder brake 14. However, in the lowering of drill stem
the cable, so as to maintain a uniform weight on the
into the hole, it is desirable to engage the clutch 11, the
over-running clutch 12 will then engage to rotate shaft 32 V drilling bit.
The inverse pressure relay 1120 is of the character
and an impeller within the hydraulic retarder 14, which
retards the descent of the drill stem, thereby enabling .35 which utilizes the “bleeding” of a small amount, of air
therefrom, which enables inverse pressure relay to func
maximum safety in going into the hole with the drill
tion at all pressures, within the range limits thereof.
So long as the drilling continues in normal formation,
However, once-the drill bit is on the bottom of the hole,
the brake 58 will maintain a uniform pressure on the
and the drilling is ready to progress, the drill stem is
lifted clear of the bottom of the hole, and the weight 40 friction elements 64 and '66 in brake ‘58, thereby retard
ing rotation of shaft 54 in proportion to this pressure.
of the load on the block is read from gauge hand 152 on
The shaft 54 is provided with sprockets 52 and 56 thereon.
weight indicator 150‘. The weight indicator is usually
The sprocket 512 is connected in geared reduction through
calibrated in thousands of pounds and is conventional, and
chain 50 with sprocket 42, which sprocket 42 is journaled
is used on practically all drilling rigs.
Once the weight of the drill stem is determined, which 45 on shaft 38. The sprocket 42 has clutch teeth 44 there
on, which teeth are engageable with teeth on clutch 46,
is known as the block load, the indicator hand 154, which
which clutch 46 is secured against relative rotation on
indicates the weight on the drill bit, is set at zero, then
shaft 38, and with the teeth of the clutches engaged, and
as the cable on the drum 4 is slackened, the indicator hand
with a sprocket 36 connected in gear reduction relation
152, which indicates the block load, will drop back to a
lesser reading, with the indicator hand 154, which indi 50 through chain 34, with a sprocket 38 on shaft 32, which
shaft 32 is connected in driving relation with drum 4, it
cates the weight on the drill bit, showing increased weight
will thus be seen, that by maintaining shaft 54 against
thereon proportionate to the weight reduction on the block
movement by the utilization of brake 58, the drum 4 will
load, with the sum total of the two weights thus indi
be held against movement, or will be permitted to “feed
cated by the hands 154 and 152 equaling the total load
at all times. The weight indicator 150 is of conventional 55 oif” at a rate proportionate to the slipping of the friction
elements 64 and 66 in brake '53. 'In this manner a uni
design and is only described as aiding in the accurate
form control of the “feed-off” of the cable from the drum
setting of the inverse pressure relay, in connection with
may be had.
the system.
If, during the course of drilling, the drill bit drills into
Different formation and different types of bits require
a cavern, which would normally let the drill stem drop,
di?erent weights for the best cutting action thereof, and
or into a soft formation which will not sustain the weight
also for the longest cutting life of the bit. With these
of the drill stem, a further device is provided to limit the
factors having been previously determined, the driller
maximum rate of downward movement of the drill stem,
knows how much weight should be placed on the bit. It
either as a free falling object or as a drill stem, with the
is at this stage of the drilling that the feed control device
is put into automatic operation.
65 drill bit thereon drilling into the soft formation, which
formation will not sustain the load weight on the bit.
The cable anchor, designated generally by the numeral
A hydraulic system is provided for the feed control
133, is so designed that, when the “dead line cable”‘142
device, whereby a hydraulic pump 90, which is prefer
is passed around the drum 13S and the lever 136 is
ably of the vane type, is connected in geared relation'by
clamped to the end 142a of the cable 142, the cable 142
is secured against lineal movement. Upon application of 70 means of sprockets 56 and 92 through a chain 24 to shaft
54,‘ and through geared reduction of sprockets and chains,
a pull load on cable 142, movement will be accorded to
lever 136 relative to arm 134, whereupon, a sensator dia
phragm member 132 will be moved. With a chamber in
to shaft 32, which in turn, interconnects with the drum
4. The'pump 91} is of the type which will withdraw hy
draulic ?uid through ?lter screen 100, through suction
the sensator diaphragm 132 ?lled with liquid, and with
the pipes 146 and 148 filled with liquid, any movement 75 pipe 96 and discharge the fluid, under pressure, outward
through pipe 1&2, and with the pressure relief valve 184
connected to pipe 102, and with pipe 1% leading from
relief valve 1&4 through metering control valve i198 to
discharge through opening 112 into reservoir 93, the de
vice is ready to operate.
The metering valve 1% is connected to pipe 162 and
tion with said drum and having a cable tension measuring
device employing a liquid body under vpressure propor
tioned to the cable tension, the improvement'comprising;
in combination, means communicating with said brake
for supplying pressurized actuating air thereto, an inverse
pressure control valve operatively associated with said
to pipe 106, and is provided with a hand wheel Hi9 so as
brake for controlling the pressure of said actuating air _ '
to enable the restriction of flow therethrough into pipe
166, which restriction likewise retards the rotation of
within said brake, said tension measuring device being
connected in controlling relation to said inverse pressure
the rotating elements in the pump 9%).
control valve for causing said inverse pressure control
However, a by
pass conduit is provided from relief valve find to connect
with 136 intermediate the metering valve 1% and the
valve to vary the pressure of said actuating air to varia
tions in the cable tension, a hydraulic pump connected in
reservoir 93. Therefore, if the ?ow of fluid through pipe
driven relation with said hoisting drum, and means de~
192 exceeds the predetermined pressure setting of valve
?ning a hydraulic ?uid circuit through said pump, said
108, the excess ?uid will be by-passed through by-pass 15 circuit including a constriction on the delivery side of said
conduit 11d into reservoir 98. By retarding the rotation
pump whereby said pump will limit the rate of ‘rotation
of the hydraulic pump 9%}, the maximum rotation of shaft
of said drum incident to the unwinding action of said
54 is predetermined, which insures maximum rotation
cable when said brake is released.
of the winding drum 4, thereby preventing the sudden
'2. In a feed control device for a rotary drilling rig,
dropping of the drill stem into a cavity, or permitting it 20 the rig having a hoisting drum for taking in and feeding
to feed off too rapidly into a soft, gummy formation in
out a terminalcable wound around said drum, an air
which the drill stem might be twisted in two.
pressure actuated brake connected in braking relation
It will be readily appreciated that the maximum rate
with said drum, and having a cable tension measuring
of rotation of the hoisting drum 4 can be readily and
device employing a liquid body under pressure propor
easily set by manually closing valve 108, while the blocks 25 tioned to the cable tension, the improvement comprising;
in combination, an air supply pipe-communicating with
are near the top of the derrick, then by opening valve
said brake for supplying actuating pressurized air there
108 to permit the ?ow of liquid therethrough, the shaft
to, an inverse pressure control valve in said pipe regu—
9-3 of the pump 99 will be permitted to rotate at a re
lating the pressure of air within said brake, said inverse
tarded rate of speed, and since the shaft of the drum 4
is in geared relation to the hydraulic pump 99, the rate 30 pressure control valve being operatively connected to
said measuring device and being controlled thereby to
of rotation of the drum 4 and the rate of descent of the
vary the air pressure Within said brake inversely with
drill stem, which is suspended by the blocks in the der
respect to variations in said cable tension, a hydraulic
rick, can be so regulated as to give the maximum rate of
travel of the drill stem in event the drill stem should en
counter a cavity or formation too soft to sustain the
weight of the drill stem.
The rate of feed-off of the cable can be readily set so
as to maintain a given load on the bit by the adjustment
of regulator wheel 121 on inverse pressure relay 120.
The cable 142 is anchored against lineal movement,
and is also anchored to lever 136 in such manner as to
impart a relative movement to the lever 136 with respect
to the arm 134, when pull is exerted on dead line cable
142, which pull will transmit reactionary pressure from
sensator diaphragm member ‘132 to and through pipes 146 '
and 148 to inverse pressure relay 126 and to weight in
dicator 159. The weight indicator 1% is of conven
tional type, and preferably has two hands thereon, one
hand 152, which indicates the full block load of the
amount of drill stem being handled by the blocks, and
the other hand 154 will indicate the actual weight on the
drill bit.
A pressure control wheel 21 is provided on pressure
relay 120, which enables the setting of the pressure relay
at a pressure to permit the brake 58 to slip to feed-off ’
cable, when the weight on the bit becomes less than the
predetermined setting of the pressure relay as determined
by the pressure control wheel 121 on relay 12%.
The setting of the inverse pressure relay 120 may be
r'etarder pump connected in geared, retarding relation
with said drum, means restricting the discharge of hy
draulic ?uid from said hydraulic retarderpump in pro
portion to the increase in speed or rotation of said drum
due to the decrease of tension on said cable by the
release of said brake.
3. In a ‘feed control device for maintaining a given
pull on a cable wound on a hoisting drum, an air actu
ated brake connected in braking relation with said hoist
ing drum, an air supply pipe operably connected to said
brake, an inverse pressure control valve within said air
supply line, a liquid pressure sensating element oper
ably connected to the weight load of said hoisting drum,
a pipe leading from said pressure sensating element to
said inverse pressure control valve in said air supply pipe,
said liquid pressure sensating element and said sensating
pipe connected thereto being preloaded with a liquid to
transmit pressure from said pressure sensating element to
said inverse pressure control valve, said inverse pres
sure control valve being responsive to liquid under pres
sure in said pressure sensating element so as to di
rect air at an inverse pressure from said air supply
pipe to said air actuated brake, a hydraulic pump con
nccted in geared relation with said hoisting drum, a
hydraulic ?uid reservoir, a pipe connected to the suc
tion side of said pump and being in ?uid communication
with said hydraulic fluid reservoir for directing hydraulic
readily accomplished by regulating the wheel 121 until 60 ?uid to said pump, a discharge pipe connected to said
‘there is no slipping of brake 58, whereupon, the pressure
pump and leading to said hydraulic ?uid reservoir, said
discharge pipe having an adjustable restriction ‘formed
therein intermediate said pump and said hydraulic fluid
reservoir, which hydraulic pump, when rotated by said
regardless of the speed of drilling, so long as the bit does 65 drum, forms a retarding element to retard the rotation
not run into a cavity or into formation too soft to sustain
of said hoisting drum when thevpressure in the pipe pre
the weight of the drill stem.
loaded with liquid has been relieved of pressure by the
Having thus described the invention, what is claimed
liquid‘ pressure sensating element to such extent that said
70 ?uid actuated brake does not retard the hoisting drum
1. In a feed control device for a rotary drilling rig,
from rotating in excess of the setting of said restriction
which rig has a hoisting drum for taking in and feeding
in the discharge line leading from said pump to said
out a terminal cable which is wound around said drum
hydraulic ?uid reservoir.
and which cable is adapted to support the weight of the
4. A feed control device for a drilling rig, said feed
drill pipe, an air actuated brake connected in braking rela 75 control device comprising a hoisting drum, a chain gear
control wheel-may be moved in one direction or the other
until slippage occurs at the desired weight on the bit.
This setting will maintain a constant weight on the bit,
reduction unit connected in driven relation with said
hoisting drum, said chain gear reduction unit having a I
driven shaft, a ‘?uid actuated brake on said driven shaft
of said gear reduction unit, a hydraulic pump retarder
mechanism connected in driven relation to said hoisting
drum through said gear reduction unit, a hydraulic ?uid
reservoir, a suction pipe leading from said hydraulic ?uid
reservoir to the suction inlet of said pump retarder mech
anism, a discharge pipe leading from the outlet of said
pump retarder mechanism to said hydraulic ?uid reser
voir, a restrictive control valve in said discharge pipe in
termediate said hydraulic pump retarder mechanism and
said hydraulic ?uid reservoir, a by-pass relief valve in
said discharge pipe and connected in parallel relation to
said restrictive control valve, which ‘by-pass Valve is set
to by-pass hydraulic ?uid into said reservoir when the
pressure exceeds the setting of said relief valve, a ?uid
pressure line connected to said ?uid actuated brake, an
inverse pressure relay valve within said line leading to
said ?uid actuated brake, a pressure sensator, and a cable
leading from said hoisting drum and being connected in
operative relation with said pressure sensator, so upon
movement of said pressure sensator, fluid pressure will
be transmitted through said pipe leading to said inverse
pressure relay valve, said ?uid actuated brake being con
nected with said sensator by said inverse pressure relay
valve in such manner that pressure on the ?uid actuated
brake will be decreased by an increased tension on said
cable and increased by a decrease in tension on said cable.
thereon; an air actuated brake, a pressure sensating ele
ment operably connected to the weight load supported
by said drilling rig hoisting drum, an air supply conduit,
an inverse pressure control valve within said air pressure
supply conduit and being intermediate said source of air
pressure supply and said air actuated brake, a liquid
loaded pipe leading from said pressure sensating element
to said inverse pressure control valve so upon increase
of pressure on said liquid loaded pipe by said pressure
sensating element, said inverse pressure control valve will
close in proportion to the increase in pressure in said
liquid loaded pipe, which will decreasev'air pressure to
said air actuated brake such proportionate amount, a
hydraulic ?uid reservoir, a positive displacement pump,
a conduit leading from said hydraulic ?uid reservoir to
the inlet side of said pump and being in communication
with said hydraulic ?uid reservoir, a discharge conduit
leading from the outlet side of said positive displacement
pump to said reservoir, a manually controlled valve with
in said discharge pipe leading from said positive displace
ment pump to said reservoir, said air actuated brake and
said positive displacement hydraulc pump'being operably
connected to said drilling rig hoisting drum so upon a de
crease of the load on said hoisting drum, said air actuated
brake will release, and upon decrease of the load on said
hoisting drum beyond a certain predetermined setting of
said manually controlled valve in said discharge line, said
manually controlled valve will impinge hydraulic ?uid
being pumped through said discharge line by said posi
tive displacement hydraulic pump to retard the rotation
5. A feed control device for drilling rig hoisting drums,
which device normally controls the feeding of the drill 30 of said pump and said drilling rig hoisting drum.
pipe into the bore hole of a well in accordance with the
References Cited in the ?le of this patent
predetermined weight on the drill bit, the formation in
said bore hole at least partially supporting the weight of
said drill pipe and said drill bit, and for retarding the 35
descent of said drill pipe in said bore hole beyond a pre
Byers _______________ __ Jan. 25, 1938
determined rate when the support of the drill pipe and
the drill bit by the formation becomes less than a prede
termined setting of the retarder to the feed control de
vice, which feed control device comprises, in combination
with a drilling rig hoisting drum having a cable spooled
Brauer ______________ __ May 10, 1938
Abraham ____________ _- Sept. 1, 1953
Des Champs __________ __ Mar. 2, 1954
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