Source: http://www.google.com/patents/US7934545?dq=ascentive
Timestamp: 2016-08-30 09:24:01
Document Index: 610142324

Matched Legal Cases: ['art 2', 'Application No. 05270083', 'art 1', 'art 2', 'art 1', 'art 2', 'Application No. 2', 'Application No. 60', 'Application No. 60']

Patent US7934545 - Rotating control head leak detection systems - Google PatentsSearch Images Maps Play YouTube News Gmail Drive More »Sign inPatentsA system and method to detect leaks in the rotating control head and a latching system to latch the rotating control head to a housing is disclosed....http://www.google.com/patents/US7934545?utm_source=gb-gplus-sharePatent US7934545 - Rotating control head leak detection systemsAdvanced Patent SearchPublication numberUS7934545 B2Publication typeGrantApplication numberUS 12/910,374Publication dateMay 3, 2011Filing dateOct 22, 2010Priority dateOct 31, 2002Fee statusPaidAlso published asCA2580177A1, CA2580177C, CA2729427A1, CA2729427C, CA2756090A1, CA2756090C, CA2756093A1, CA2756093C, EP1830034A2, EP1830034A3, EP2631419A1, EP2636841A1, EP2636841B1, EP2639400A1, US7836946, US8113291, US8353337, US8714240, US20060144622, US20110036629, US20110168382, US20120138366, US20130192896Publication number12910374, 910374, US 7934545 B2, US 7934545B2, US-B2-7934545, US7934545 B2, US7934545B2InventorsThomas F. Bailey, James W. ChambersOriginal AssigneeWeatherford/Lamb, Inc.Export CitationBiBTeX, EndNote, RefManPatent Citations (533), Non-Patent Citations (199), Referenced by (5), Classifications (13), Legal Events (3) External Links: USPTO, USPTO Assignment, EspacenetRotating control head leak detection systems
US 7934545 B2Abstract
A system and method to detect leaks in the rotating control head and a latching system to latch the rotating control head to a housing is disclosed.
1. A method for comparing fluid to and from a latch assembly for latching a rotating control head, comprising the steps of:
delivering a fluid to a first side of a piston for moving the piston from a first position to a second position;
measuring a volume of fluid delivered to the first side of the piston to produce a measured first fluid volume value;
communicating the fluid from a second side of the piston;
measuring a volume of fluid from the second side of the piston to produce a measured second fluid volume value; and
comparing the measured first fluid volume value to the measured second fluid volume value.
2. The method of claim 1, wherein the step of measuring a volume of fluid to the first side of the piston comprising the steps of:
measuring the fluid with a totalizing flow meter; and
reading the totalizing flow meter to produce the measured fluid volume value.
3. A method for comparing fluid to and from a latch assembly for latching a rotating control head, comprising the steps of:
measuring a volume of fluid delivered to the first side of the piston with a first totalizing flow meter to produce a measured first fluid volume value;
measuring a volume of fluid from the second side of the piston with a second totalizing flow meter to produce a measured second fluid volume value; and
4. A method for use of a rotating control head having a bearing assembly for rotating while drilling, comprising the steps of:
positioning a chamber in the bearing assembly;
forming a first opening into the chamber;
forming a second opening into the chamber;
delivering a fluid to the first opening;
communicating the fluid from the second opening;
measuring a flow value of the fluid to the first opening;
measuring a flow value of the fluid from the second opening; and
comparing the measured flow value to the first opening to the measured flow value from the second opening.
5. The method of claim 4, wherein the step of measuring a flow value of the fluid to the first opening comprising the steps of:
measuring the flow rate to the first opening with a first flow meter; and
reading the first flow meter to produce a measured first flow rate value.
6. The method of claim 5, wherein the step of measuring a flow value of the fluid to the first opening comprising the steps of:
measuring the flow rate from the second opening with a second flow meter; and
reading the second flow meter to produce a measured second flow rate value.
7. The method of claim 6, wherein the step of comparing the measured flow value comprising the step of:
comparing the measured first flow rate value to the first opening to the measured second flow rate value from the second opening.
8. The method of claim 4, wherein the step of measuring a flow value of the fluid to the first opening comprising the steps of:
measuring the flow volume with a first flow meter; and
reading the first flow meter to produce a measured first flow volume value.
9. The method of claim 8, wherein the step of measuring a flow value of the fluid from the second opening comprising the steps of:
measuring the flow volume with a second flow meter; and
reading the second flow meter to produce a measured second flow volume value.
10. The method of claim 9, wherein the step of comparing the measured flow value comprising the step of:
comparing the measured first flow volume value to the measured second flow volume value.
determining if the measured flow value to the first opening is in a predetermined tolerance to the measured flow value from the second opening.
activating an alarm if the measured flow value is determined to be out of a predetermined tolerance to the measured flow value from the second opening.
displaying a text message on a monitor if the measured flow value is determined to be out of a predetermined tolerance to the measured flow value from the second opening.
14. A method for use in a drilling operation, comprising the steps of:
positioning a chamber in a housing;
15. The method of claim 14, wherein the step of measuring a flow value of the fluid to the first opening comprising the steps of:
16. The method of claim 15, wherein the step of measuring a flow value of the fluid to the first opening comprising the steps of:
reading the second flow meter to produce a measured flow rate value.
17. The method of claim 16, wherein the step of comprising the measured flow value comprising the step of:
18. The method of claim 14, wherein the step of measuring a flow value of the fluid to the first opening comprising the steps of:
19. The method of claim 18, wherein the step of measuring a flow value of the fluid from the second opening comprising the steps of:
20. The method of claim 19, wherein the step of comparing the measured flow value comprising the step of:
This application is a divisional of co-pending U.S. application Ser. No. 11/366,078, filed Mar. 2, 2006, which is a continuation-in-part of U.S. application Ser. No. 10/285,336 entitled “Active/Passive Seal Rotating Control Head” filed Oct. 31, 2002 (now issued as U.S. Pat. No. 7,040,394 on May 9, 2006), and U.S. application Ser. No. 10/995,980 entitled “Riser Rotating Control Device” filed Nov. 23, 2004 (now issued as U.S. Pat. No. 7,487,837 on Feb. 10, 2009), all of which are incorporated by reference in their entirety for all purposes.
Embodiments of the present invention relate generally to a method and a system for a rotating control head used in a drilling operation. More particularly, the invention relates to a remote leak detection system, radial seal protection system and an improved cooling system for a rotating control head and a method for using the systems. The present invention also includes a leak detection system for a latch system to latch the rotating control device to a housing.
Drilling a wellbore for hydrocarbons requires significant expenditures of manpower and equipment. Thus, constant advances are being sought to reduce any downtime of equipment and expedite any repairs that become necessary. Rotating equipment requires maintenance as the drilling environment produces forces, elevated temperatures and abrasive cuttings detrimental to the longevity of seals, bearings, and packing elements.
In a typical drilling operation, a drill bit is attached to a drill pipe. Thereafter, a drive unit rotates the drill pipe through a drive member, referred to as a kelly as the drill pipe and drill bit are urged downward to form the wellbore. In some arrangements, a kelly is not used, thereby allowing the drive unit to attach directly to the drill pipe or tubular. The length of the wellbore is determined by the location of the hydrocarbon formations. In many instances, the formations produce fluid pressure that may be a hazard to the drilling crew and equipment unless properly controlled.
Several components are used to control the fluid pressure. Typically, one or more blowout preventers (BOP) are mounted with the well forming a BOP stack to seal the well. In particular, an annular BOP is used to selectively seal the lower portions of the well from a tubular that allows the discharge of mud. In many instances, a conventional rotating control head is mounted above the BOP stack. An inner portion or member of the conventional rotating control head is designed to seal and rotate with the drill pipe. The inner portion or member typically includes at least one internal sealing element mounted with a plurality of bearings in the rotating control head.
The internal sealing element may consist of either one, two or both of a passive seal assembly and/or an active seal assembly. The active seal assembly can be hydraulically or mechanically activated. Generally, a hydraulic circuit provides hydraulic fluid to the active seal in the rotating control head. The hydraulic circuit typically includes a reservoir containing a supply of hydraulic fluid and a pump to communicate the hydraulic fluid from the reservoir to the rotating control head. As the hydraulic fluid enters the rotating control head, a pressure is created to energize the active seal assembly. Preferably, the pressure in the active seal assembly is maintained at a greater pressure than the wellbore pressure. Typically, the hydraulic circuit receives input from the wellbore and supplies hydraulic fluid to the active seal assembly to maintain the desired pressure differential.
During the drilling operation, the drill pipe or tubular is axially and slidably moved through the rotating control head. The axial movement of the drill pipe along with other forces experienced in the drilling operation, some of which are discussed below, causes wear and tear on the bearing and seal assembly and the assembly subsequently requires repair. Typically, the drill pipe or a portion thereof is pulled from the well and the bearing and seal assembly in the rotating control head is then released. Thereafter, an air tugger or other lifting means in combination with a tool joint on the drill string can be used to lift the bearing and seal assembly from the rotating control head. The bearing and seal assembly is replaced or reworked, the bearing and seal assembly installed into the rotating control head, and the drilling operation is resumed.
The thrust generated by the wellbore fluid pressure, the radial forces on the bearing assembly and other forces cause a substantial amount of heat to build in the conventional rotating control head. The heat causes the seals and bearings to wear and subsequently require repair. The conventional rotating control head typically includes a cooling system that circulates fluid through the seals and bearings to remove the heat.
Cooling systems have been known in the past for rotating control heads and rotating blowout preventers. For example, U.S. Pat. Nos. 5,178,215, 5,224,557 and 5,277,249 propose a heat exchanger for cooling hydraulic fluid to reduce the internal temperature of a rotary blowout preventer to extend the operating life of various bearing and seal assemblies found therein.
FIG. 10 discloses a system where hydraulic fluid moves through the seal carrier C of a rotating control head, generally indicated at RCH, in a single pass to cool top radial seals S1 and S2 but with the fluid external to the bearing section B. Similarly, U.S. Pat. No. 5,662,181, assigned to the assignee of the present invention, discloses use of first inlet and outlet fittings for circulating a fluid, i.e. chilled water and/or antifreeze, to cool top radial seals in a rotating control head. A second lubricant inlet fitting is used for supplying fluid for lubricating not only the top radial seals but also top radial bearings, thrust bearings, bottom radial bearings and bottom radial seals all positioned beneath the top radial seals. (See '181 patent, col. 5, ln. 42 to col. 6, ln. 10 and col. 7, lns. 1-10.) These two separate fluids require their own fluid flow equipment, including hydraulic/pneumatic hoses.
Also, U.S. Pat. No. 5,348,107 proposes means for circulating lubricant around and through the interior of a drilling head. More particularly, FIGS. 3 to 6 of the '107 patent propose circulating lubricant to seals via a plurality of passageways in the packing gland. These packing gland passageways are proposed to be in fluid communication with the lubricant passageways such that lubricant will freely circulate to the seals. (See '107 patent, col. 3, lns. 27-65.)
U.S. Pat. Nos. 6,554,016 and 6,749,172, assigned to the assignee of the present invention, propose a rotary blowout preventer with a first and a second fluid lubricating, cooling and filtering circuit separated by a seal. Adjustable orifices are proposed connected to the outlet of the first and second fluid circuits to control pressures within the circuits. Such pressures are stated to affect the wear rates of the seals and to control the wear rate of one seal relative to another seal.
Therefore, an improved system for cooling radial seals and the bearing section of a rotating control head with one fluid is desired. If the radial seals are not sufficiently cooled, the localized temperature at the sealing surface will rise until the temperature limitations of the seal material is reached and degradation of the radial seal begins. The faster the rise in temperature means less life for the radial seals. In order to obtain sufficient life from radial seals, the rate of heat extraction should be fast enough to allow the temperature at the sealing surface to level off at a temperature lower than that of the seal material's upper limit.
Also, to protect the radial seals in a rotating control head, it would be desirable to regulate the differential pressure across the upper top radial seal that separates the fluid from the environment. Typically, fluid pressure is approximately 200 psi above the wellbore pressure. This pressure is the differential pressure across the upper top radial seal. Radial seals have a PV factor, which is differential pressure across the seal times the rotary velocity of the inner portion or member of the rotating control head in surface feet per minute. When this value is exceeded, the radial seal fails prematurely. Thus, the PV factor is the limitation to the amount of pressure and RPM that a rotating control head can be expected to perform. When the PV factor is exceeded, either excessive heat is generated by friction of the radial seals on the rotating inner member, which causes the seal material to break down, or the pressure forces the radial seal into the annular area between the rotating inner member and stationary outer member which damages the deformed seal.
In general, this PV seal problem has been addressed by limiting the RPM, pressure or both in a rotating control head. The highest dynamic, but rarely experienced, rating on a rotating control head is presently approximately 2500 psi. Some companies publish life expectancy charts which will provide the expected life of a radial seal for a particular pressure and RPM value. An annular labyrinth ring has also been used in the past between the lubricant and top radial seal to reduce the differential pressure across the top radial seal. Pressure staging and cooling of seals has been proposed in U.S. Pat. No. 6,227,547, assigned on its face to Kalsi Engineering, Inc. of Sugar Land, Tex.
Furthermore, U.S. Pat. No. 7,487,837 discloses in FIG. 14 a remote control display 1400 having a hydraulic fluid indicator 1488 to indicate a fluid leak condition. FIG. 18 of the '980 application further discloses that the alarm indicator 1480 and horn are activated based in part on the fluid leak indicator 1488 being activated for a predetermined time.
The above discussed U.S. Pat. Nos. 5,178,215; 5,224,557; 5,277,249; 5,348,107; 5,662,181; 6,227,547; 6,554,016; and 6,749,172 are incorporated herein by reference in their entirety for all purposes.
There is a need therefore, for an improved, cost-effective rotating control head that reduces repairs to the seals in the rotating control head and an improved leak detection system to indicate leaks pass these seals. There is a further need for a cooling system in a rotating control head for top radial seals that can be easily implemented and maintained. There is yet a further need for an improved rotating control head where the PV factor is reduced by regulating the differential pressure across the upper top radial seal. There is yet a further need for an improved leak detection system for the rotating control head and its latching system.
The present invention generally relates to a system and method for reducing repairs to a rotating control head and a system and method to detect leaks in the rotating control head and its latching system.
In particular, the present invention relates to a system and method for cooling a rotating control head while regulating the pressure on the upper top radial seal in the rotating control head to reduce, its PV factor. The improved rotating control head includes an improved cooling system using one fluid to cool the radial seals and bearings in combination with a reduced PV factor radial seal protection system.
A leak detection system and method of the present invention uses a comparator to compare fluid values in and from the latch assembly of the latch system and/or in and from the bearing section or system of the rotating control head.
In another aspect, a system and method for sealing a tubular in a rotating control head is provided. The method includes supplying fluid to the rotating control head and activating a seal arrangement to seal around the tubular. The system and method further includes passing a cooling medium through the rotating control head while maintaining a pressure differential between a fluid pressure in the rotating control head and a wellbore pressure.
So that the manner in which the above recited features of the present invention can be understood in detail, a more particular description of the invention, briefly summarized above, may be had by reference to embodiments, some of which are illustrated in the appended drawings. It is to be noted, however, that the appended drawings illustrate only typical embodiments of this invention and are therefore not to be considered limiting of its scope, for the invention may be used in other equally effective embodiments.
FIG. 1 is an elevational section view illustrating a rotating control head having an active seal assembly positioned above a passive seal assembly latched in a housing in accord with the present invention.
FIG. 2A illustrates a rotating control head cooled by a heat exchanger.
FIG. 2B illustrates a schematic view of the heat exchanger.
FIG. 3A illustrates a rotating control head cooled by flow a gas.
FIG. 3B illustrates a schematic view of the gas in a substantially circular passageway.
FIG. 4A illustrates a rotating control head cooled by a fluid mixture.
FIG. 4B illustrates a schematic view of the fluid mixture circulating in a substantially circular passageway.
FIG. 5A illustrates the rotating control head cooled by a refrigerant.
FIG. 5B illustrates a schematic view of the refrigerant circulating in a substantially circular passageway.
FIG. 6 illustrates a rotating control head actuated by a piston intensifier in communication with the wellbore pressure.
FIG. 7A illustrates an alternative embodiment of a rotating control head with a passive seal assembly and an active seal assembly mechanical annular blowout preventer (BOP) in an unlocked position.
FIG. 7B illustrates the rotating control head of FIG. 7A with the annular BOP in a locked position.
FIG. 8 illustrates an alternative embodiment of a rotating control head with a passive seal assembly positioned above an active seal assembly in accord with the present invention.
FIG. 9 is an elevational section view showing a rotating control head with two passive seal assemblies latched in a housing in accord with the present invention.
FIG. 10 is an enlarged section view of a prior art rotating control head system where cooling fluid moves through the seal carrier in a single pass but with the fluid external to the bearing section.
FIG. 11 is an enlarged section view of a rotating control head cooling system where air moves through a passageway similar to the passageway shown in above FIGS. 2A and 2B.
FIG. 12 is an enlarged section view of a rotating control head where hydraulic fluid moves through the seal carrier to cool the top radial seals in a single pass.
FIG. 13 is an enlarged section view showing staging pressure on radial seals for a rotating control head in accord with the present invention, including regulating pressure between an upper top radial seal and a high flow lower top radial seal.
FIG. 14 is an enlarged section view of a multi-pass heat exchanger for a rotating control head in accord with the present invention where a hydraulic fluid is both moved through the bearing section and makes multiple passes around the radial seals.
FIGS. 15A and 15B are schematics of the preferred hydraulic system for the present invention.
FIG. 16 is a flowchart for operation of the hydraulic system of FIG. 15 of the present invention.
FIG. 18A is a continuation of the flowchart of FIG. 17.
FIG. 18B is a continuation of the flowchart of FIG. 18A.
FIG. 19 is a flowchart of a subroutine for controlling the pressure in the bearing section of the rotating control head of the present invention.
FIG. 20 is a continuation of the flowchart of FIG. 19.
FIG. 21 is a continuation of the flowchart of FIG. 20.
FIG. 22 is a continuation of the flowchart of FIG. 21.
FIG. 23 is a flowchart of a subroutine for controlling either the pressure of the latching system in the housing, such as shown in FIGS. 1 and 9, or the pressure on the radial seals, as shown in FIG. 13, of the present invention.
FIG. 24 is a continuation of the flowchart of FIG. 23.
FIG. 25 is a plan view of a control console in accord with the present invention.
FIG. 26 is an enlarged elevational section view of a latch assembly in the latched position with a perpendicular port communicating above a piston indicator valve that is shown in a closed position.
FIG. 27 is a view similar to FIG. 26 but taken at a different section cut to show another perpendicular port communicating below the closed piston indicator valve.
Generally, the present invention relates to a rotating control head for use with a drilling rig. Typically, an inner portion or member of the rotating control head is designed to seal around a rotating tubular and rotate with the tubular by use of an internal sealing element and bearings. Additionally, the inner portion of the rotating control head Permits the tubular to move axially and slidably through the rotating control head on the drilling rig.
FIG. 1 is a cross-sectional view illustrating the rotating control head, generally indicated at 100, in accord with the present invention. The rotating control head 100 preferably includes an active seal assembly 105 and a passive seal assembly 110. Each seal assembly 105, 110 includes components that rotate with respect to a housing 115. The components that rotate in the rotating control head are mounted for rotation about a plurality of bearings 125.
As depicted, the active seal assembly 105 includes a bladder support housing 135 mounted within the plurality of bearings 125. The bladder support housing 135 is used to mount bladder 130. Under hydraulic pressure, as discussed below, bladder 130 moves radially inward to seal around a tubular, such as a drilling pipe or tubular (not shown). In this manner, bladder 130 can expand to seal off a borehole using the rotating control head 100.
As illustrated in FIG. 1, upper and lower caps 140, 145 fit over the respective upper and lower end of the bladder 130 to secure the bladder 130 within the bladder support housing 135. Typically, the upper and lower caps 140, 145 are secured in position by a setscrew (not shown). Upper and lower seals 155, 160 seal off chamber 150 that is preferably defined radially outwardly of bladder 130 and radially inwardly of bladder support housing 135.
Generally, fluid is supplied to the chamber 150 under a controlled pressure to energize the bladder 130. A hydraulic control will be illustrated and discussed in FIGS. 2-6. Essentially, the hydraulic control maintains and monitors hydraulic pressure within pressure chamber 150. Hydraulic pressure P1 is preferably maintained by the hydraulic control between 0 to 200 psi above a wellbore pressure P2. The bladder 130 is constructed from flexible material allowing bladder surface 175 to press against the tubular at approximately the same pressure as the hydraulic pressure P1. Due to the flexibility of the bladder, it also may conveniently seal around irregular shaped tubular string, such as a hexagonal kelly. In this respect, the hydraulic control maintains the differential pressure between the pressure chamber 150 at pressure P1 and wellbore pressure P2. Additionally, the active seal assembly 105 includes support fingers 180 to support the bladder 130 at the most stressful area of the seal between the fluid pressure P1 and the ambient pressure.
The hydraulic control may be used to de-energize the bladder 130 and allow the active seal assembly 105 to release the seal around the tubular. Generally, fluid in the chamber 150 is drained into a hydraulic reservoir (not shown), thereby reducing the pressure P1. Subsequently, the bladder surface 175 loses contact with the tubular as the bladder 130 becomes de-energized and moves radially outward. In this manner, the seal around the tubular is released allowing the tubular to be removed from the rotating control head 100.
In the embodiment shown in FIG. 1, the passive seal assembly 110 is operatively attached to the bladder support housing 135, thereby allowing the passive seal assembly 110 to rotate with the active seal assembly 105. Fluid is not required to operate the passive seal assembly 110 but rather it utilizes pressure P2 to create a seal around the tubular. The passive seal assembly 110 is constructed and arranged in an axially downward conical shape, thereby allowing the pressure P2 to act against a tapered surface 195 to close the passive seal assembly 110 around the tubular. Additionally, the passive seal assembly 110 includes an inner diameter 190 smaller than the outer diameter of the tubular to provide an interference fit between the tubular and the passive seal assembly 110.
FIG. 2A illustrates a rotating control head 200 cooled by heat exchanger 205. As shown, the rotating control head 200 is depicted generally to illustrate this embodiment of the invention, thereby applying this embodiment to a variety of different types of rotating control heads. A hydraulic control 210 provides fluid to the rotating control head 200. The hydraulic control 210 typically includes a reservoir 215 to contain a supply of fluid, a pump 220 to communicate the fluid from the reservoir 215 to the rotating control head 200 and a valve 225 to remove excess pressure in the rotating control head 200.
Generally, the hydraulic control 210 provides fluid to energize a bladder 230 and lubricate a plurality of bearings 255. As the fluid enters a port 235, the fluid is communicated to the plurality of bearings 255 and a chamber 240. As the chamber 240 fills with a fluid, pressure P1 is created. The pressure P1 acts against the bladder 230 causing the bladder 230 to expand radially inward to seal around a tubular string (not shown). Typically, the pressure P1 is maintained between 0-200 psi above a wellbore pressure P2.
The rotating control head 200 is cooled by the heat exchanger 205. The heat exchanger 205 is constructed and arranged to remove heat from the rotating control head 200 by introducing a gas, such as air, at a low temperature into an inlet 265 and thereafter transferring heat energy from a plurality of radial seals 275A and 275B and the plurality of bearings 255 to the gas as the gas passes through the heat exchanger 205. Subsequently, the gas at a higher temperature exits the heat exchanger 205 through an outlet 270. Typically, gas is pumped into the inlet 265 by a blowing apparatus (not shown). However, other means of communicating gas to the inlet 265 may be employed, so long as they are capable of supplying a sufficient amount of gas to the heat exchanger 205.
FIG. 2B illustrates a schematic view of the heat exchanger 205. As illustrated, the heat exchanger 205 comprises a passageway 280 with a plurality of substantially square curves. The passageway 280 is arranged to maximize the surface area covered by the heat exchanger 205. The low temperature gas entering the inlet 265 flows through the passageway 280 in the direction illustrated by arrow 285. As the gas circulates through the passageway 280, the gas increases in temperature as the heat from the rotating control head 200 is transferred to the gas. The high temperature gas exits the outlet 270 as indicated by the direction of arrow 285. In this manner, the heat generated by the rotating control head 200 is transferred to the gas passing through the heat exchanger 205.
FIG. 3A illustrates a rotating control head 300 cooled by a gas. As shown, the rotating control head 300 is depicted generally to illustrate this embodiment of the invention, thereby applying this embodiment to a variety of different types of rotating control heads. A hydraulic control 310 supplies fluid to the rotating control head 300. The hydraulic control 310 typically includes a reservoir 315 to contain a supply of fluid and a pump 320 to communicate the fluid from the reservoir 315 to the rotating control head 300. Additionally, the hydraulic control 310 includes a valve 345 to relieve excess pressure in the rotating control head 300.
Generally, the hydraulic control 310 supplies fluid to energize a bladder 330 and lubricate a plurality of bearings 355. As the fluid enters a port 335, a portion is communicated to the plurality of bearings 355 and another portion is used to fill a chamber 340. As the chamber 340 fills with a fluid, a pressure P1 is created. Pressure P1 acts against the bladder 330 causing the bladder 330 to move radially inward to seal around a tubular (not shown). Typically, the pressure P1 is maintained between 0 to 200 psi above a wellbore pressure P2. If the wellbore pressure P2 drops, the pressure P1 may be relieved through valve 345 by removing a portion of the fluid from the chamber 340.
The rotating control head 300 is cooled by a flow of gas through a substantially circular passageway 380 through an upper portion of the rotating control head 300. The circular passageway 380 is constructed and arranged to remove heat from the rotating control head 300 by introducing a gas, such as air, at a low temperature into an inlet 365, transferring heat energy to the gas and subsequently allowing the gas at a high temperature to exit through an outlet 370. The heat energy is transferred from a plurality of radial seals 375A and 375B and the plurality of bearings 355 as the gas passes through the circular passageway 380. Typically, gas is pumped into the inlet 365 by a blowing apparatus (not shown). However, other means of communicating gas to the inlet 365 may be employed, so long as they are capable of supplying a sufficient amount of gas to the substantially circular passageway 380.
FIG. 3B illustrates a schematic view of the gas passing through the substantially circular passageway 380. The circular passageway 380 is arranged to maximize the surface area covered by the circular passageway 380. The low temperature gas entering the inlet 365 flows through the circular passageway 380 in the direction illustrated by arrow 385. As the gas circulates through the circular passageway 380, the gas increases in temperature as the heat from the rotating control head 300 is transferred to the gas. The high temperature gas exits the outlet 370 as indicated by the direction of arrow 385. In this manner, the heat generated by the rotating control head 300 is removed allowing the rotating control head 300 to function properly.
In an alternative embodiment, the rotating control head 300 may operate without the use of the circular passageway 380. In other words, the rotating control head 300 would function properly without removing heat from the plurality of radial seals 375A and 375B and the plurality of bearings 355. This alternative embodiment typically applies when the wellbore pressure P2 is relatively low.
FIGS. 4A and 4B illustrate a rotating control head 400 cooled by a fluid mixture. As shown, the rotating control head 400 is depicted generally to illustrate this embodiment of the invention, thereby applying this embodiment to a variety of different types of rotating control heads. A hydraulic control 410 supplies fluid to the rotating control head 400. The hydraulic control 410 typically includes a reservoir 415 to contain a supply of fluid and a pump 420 to communicate the fluid from the reservoir 415 to the rotating control head 400. Additionally, the hydraulic control 410 includes a valve 445 to relieve excess pressure in the rotating control head 400. In the same manner as the hydraulic control 310, the hydraulic control 410 supplies fluid to energize a bladder 430 and lubricate a plurality of bearings 455.
The rotating control head 400 is cooled by a fluid mixture circulated through a substantially circular passageway 480 on an upper portion of the rotating control head 400. In the embodiment shown, the fluid mixture preferably consists of water or a water-glycol mixture. However, other mixtures of fluid may be employed, so long as, the fluid mixture has the capability to circulate through the circular passageway 480 and reduce the heat in the rotating control head 400.
The circular passageway 480 is constructed and arranged to remove heat from the rotating control head 400 by introducing the fluid mixture at a low temperature into an inlet 465, transferring heat energy to the fluid mixture and subsequently allowing the fluid mixture at a high temperature to exit through an outlet 470. The heat energy is transferred from a plurality of radial seals 475A and 475B and the plurality of bearings 455 as the fluid mixture circulates through the circular passageway 480. The fluid mixture is preferably pumped into the inlet 465 through a fluid circuit 425. The fluid circuit 425 is comprised of a reservoir 490 to contain a supply of the fluid mixture and a pump 495 to circulate the fluid mixture through the rotating control head 400.
FIG. 4B illustrates a schematic view of the fluid mixture circulating in the substantially circular passageway 480. The circular passageway 480 is arranged to maximize the surface area covered by the circular passageway 480. The low temperature fluid entering the inlet 465 flows through the circular passageway 480 in the direction illustrated by arrow 485. As the fluid circulates through the circular passageway 480, the fluid increases in temperature as the heat from the rotating control head 400 is transferred to the fluid. The high temperature fluid exits out the outlet 470 as indicated by the direction of arrow 485. In this manner, the heat generated by the rotating control head 400 is removed allowing the rotating control head 400 to function properly.
FIGS. 5A and 5B illustrate a rotating control head 500 cooled by a refrigerant. As shown, the rotating control head 500 is depicted generally to illustrate this embodiment of the invention, thereby applying this embodiment to a variety of different types of rotating control heads. A hydraulic control 510 supplies fluid to the rotating control head 500. The hydraulic control 510 typically includes a reservoir 515 to contain a supply of fluid and a pump 520 to communicate the fluid from the reservoir 515 to the rotating control head 500. Additionally, the hydraulic control 510 includes a valve 545 to relieve excess pressure in the rotating control head 500. In the same manner as the hydraulic control 310, the hydraulic control 510 supplies fluid to energize a bladder 530 and lubricate a plurality of bearings 555.
The rotating control head 500 is cooled by a refrigerant circulated through a substantially circular passageway 580 in an upper portion of the rotating control head 500. The circular passageway 580 is constructed and arranged to remove heat from the rotating control head 500 by introducing the refrigerant at a low temperature into an inlet 565, transferring heat energy to the refrigerant and subsequently allowing the refrigerant at a high temperature to exit through an outlet 570. The heat energy is transferred from a plurality of radial seals 575A and 575B and the plurality of bearings 555 as the refrigerant circulates through the circular passageway 580. The refrigerant is preferably communicated into the inlet 565 through a refrigerant circuit 525. The refrigerant circuit 525 includes a reservoir 590 containing a supply of vapor refrigerant. A compressor 595 draws the vapor refrigerant from the reservoir 590 and compresses the vapor refrigerant into a liquid refrigerant. Thereafter, the liquid refrigerant is communicated to an expansion valve 560. At this point, the expansion valve 560 changes the low temperature liquid refrigerant into a low temperature vapor refrigerant as the refrigerant enters inlet 565.
FIG. 5B illustrates a schematic view of the vapor refrigerant circulating in the substantially circular passageway 580. The circular passageway 580 is arranged in an approximately 320-degree arc to maximize the surface area covered by the circular passageway 580. The low temperature vapor refrigerant entering the inlet 565 flows through the circular passageway 580 in the direction illustrated by arrow 585. As the vapor refrigerant circulates through the circular passageway 580, the vapor refrigerant increases in temperature as the heat from the rotating control head 500 is transferred to the vapor refrigerant. The high temperature vapor refrigerant exits out the outlet 570 as indicated by the direction of arrow 585. Thereafter, the high temperature vapor refrigerant rejects the heat to the environment through a heat exchanger (not shown) and returns to the reservoir 590. In this manner, the heat generated by the rotating control head 500 is removed allowing the rotating control head 500 to function properly.
FIG. 6 illustrates a rotating control head 600 actuated by a piston intensifier circuit 610 in communication with a wellbore 680. As shown, the rotating control head 600 is depicted generally to illustrate this embodiment of the invention, thereby applying this embodiment to a variety of different types of rotating control heads. The piston intensifier circuit 610 supplies fluid to the rotating control head 600. The piston intensifier circuit 610 typically includes a housing 645 and a piston arrangement 630. The piston arrangement, generally indicated at 630, is formed from a larger piston 620 and a smaller piston 615. The pistons 615, 620 are constructed and arranged to maintain a pressure differential between a hydraulic pressure P1 and a wellbore pressure P2. In other words, the pistons 615, 620 are designed with a specific surface area ratio to maintain about a 200 psi pressure differential between the hydraulic pressure P1 and the wellbore pressure P2, thereby allowing the P1 to be 200 psi higher than P2. The piston arrangement 630 is disposed in the housing 645 to form an upper chamber 660 and lower chamber 685. Additionally, a plurality of seal members 605, 606 are disposed around the pistons 615, 620, respectively, to form a fluid tight seal between the chambers 660, 685.
The piston intensifier circuit 610 mechanically provides hydraulic pressure P1 to energize a bladder 650. Initially, fluid is filled into upper chamber 660 and is thereafter sealed. The wellbore fluid from the wellbore 680 is in fluid communication with lower chamber 685. Therefore, as the wellbore pressure P2 increases more wellbore fluid is communicated to the lower chamber 685 creating a pressure in the lower chamber 685. The pressure in the lower chamber 685 causes the piston arrangement 630 to move axially upward forcing fluid in the upper chamber 660 to enter port 635 and pressurize a chamber 640. As the chamber 640 fills with a fluid, the pressure P1 increases causing the bladder 650 to move radially inward to seal around a tubular (not shown). In this manner, the bladder 650 is energized allowing the rotating control head 600 to seal around a tubular.
A fluid, such as water-glycol, is circulated through the rotating control head 600 by a fluid circuit 625. Typically, heat on the rotating control head 600 is removed by introducing the fluid at a low temperature into an inlet 665, transferring heat energy to the fluid and subsequently allowing the fluid at a high temperature to exit through an outlet 670. The heat energy is transferred from a plurality of radial seals 675A and 675B and the plurality of bearings 655 as the fluid circulates through the rotating control head 600. The fluid is preferably pumped into the inlet 665 through the fluid circuit 625. Generally, the circuit 625 comprises a reservoir 690 to contain a supply of the fluid and a pump 695 to circulate the fluid through the rotating control head 600.
In another embodiment, the piston intensifier circuit 610 is in fluid communication with a nitrogen gas source (not shown). In this embodiment, a pressure transducer (not shown) measures the wellbore pressure P2 and subsequently injects nitrogen into the lower chamber 685 at the same pressure as pressure P2. The nitrogen pressure in the lower chamber 685 may be adjusted as the wellbore pressure P2 changes, thereby maintaining the desired pressure differential between hydraulic pressure P1 and wellbore pressure P2.
FIG. 7A illustrates an alternative embodiment of a rotating control head 700 in an unlocked position. The rotating control head 700 is arranged and constructed in a similar manner as the rotating control head 100 shown on FIG. 1. Therefore, for convenience, similar components that function in the same manner will be labeled with the same numbers as the rotating control head 100. The primary difference between the rotating control head 700 and rotating control head 100 is the active seal assembly.
As shown in FIG. 7A, the rotating control head 700 includes an active seal assembly, generally indicated at 705. The active seal assembly 705 includes a primary seal 735 that moves radially inward as a piston 715 wedges against a tapered surface of the seal 735. The primary seal 735 is constructed from flexible material to permit sealing around irregularly shaped tubular string such as a hexagonal kelly. The upper end of the seal 735 is connected to a top ring 710.
The active sealing assembly 705 includes an upper chamber 720 and a lower chamber 725. The upper chamber 720 is formed between the piston 715 and a piston housing 740. To move the rotating control head 700 from an unlocked or relaxed position to a locked or sealed position, fluid is pumped through port 745 into an upper chamber 720. As fluid fills the upper chamber 720, the pressure created acts against the lower end of the piston 715 and urges the piston 715 axially upward towards the top ring 710. At the same time, the piston 715 wedges against the tapered portion of the primary seal 735 causing the seal 735 to move radially inward to seal against the tubular (not shown). In this manner, the active seal assembly 705 is in the locked or sealed position as illustrated in FIG. 7B.
As shown on FIG. 7B, the piston 715 has moved axially upward contacting the top ring 710 and the primary seal 735 has moved radially inward. To move the active seal assembly 705 from the locked position to the unlocked position, fluid is pumped through port 755 into the lower chamber 725. As the chamber fills up, the fluid creates a pressure that acts against surface 760 to urge the piston 715 axially downward, thereby allowing the primary seal 735 to move radially outward, as shown on FIG. 7A.
FIG. 8 illustrates an alternative embodiment of a rotating control head 800 in accord with the present invention. The rotating control head 800 is constructed from similar components as the rotating control head 100, as shown on FIG. 1. Therefore, for convenience, similar components that function in the same manner will be labeled with the same numbers as the rotating control head 100. The primary difference between the rotating control head 800 and rotating control head 100 is the location of the active seal assembly 105 and the passive seal assembly 110.
As shown in FIG. 8, the passive seal assembly 110 is disposed above the active seal assembly 105. The passive seal assembly 110 is operatively attached to the bladder support housing 135, thereby allowing the passive seal assembly 110 to rotate with the active seal assembly 105. The passive seal assembly 110 is constructed and arranged in an axially downward conical shape, thereby allowing the pressure in the rotating control head 800 to act against the tapered surface 195 and close the passive seal assembly 110 around the tubular (not shown). Additionally, the passive seal assembly 110 includes the inner diameter 190, which is smaller than the outer diameter of the tubular to allow an interference fit between the tubular and the passive seal assembly 110.
As depicted, the active seal assembly 105 includes the bladder support housing 135 mounted on the plurality of bearings 125. The bladder support housing 135 is used to mount bladder 130. Under hydraulic pressure, bladder 130 moves radially inward to seal around a tubular such as a drilling tubular (not shown). Generally, fluid is supplied to the chamber 150 under a controlled pressure to energize the bladder 130. Essentially, a hydraulic control (not shown) maintains and monitors hydraulic pressure within pressure chamber 150. Hydraulic pressure P1 is preferably maintained by the hydraulic control between 0 to 200 psi above a wellbore pressure P2. The bladder 130 is constructed from flexible material allowing bladder surface 175 to press against the tubular at approximately the same pressure as the hydraulic pressure P1.
The hydraulic control may be used to de-energize the bladder 130 and allow the active seal assembly 105 to release the seal around the tubular. Generally, the fluid in the chamber 150 is drained into a hydraulic reservoir (not shown), thereby reducing the pressure P1. Subsequently, the bladder surface 175 loses contact with the tubular as the bladder 130 becomes de-energized and moves radially outward. In this manner, the seal around the tubular is released allowing the tubular to be removed from the rotating control head 800.
FIG. 9 illustrates another alternative embodiment of a rotating control head, generally indicated at 900. The rotating control head 900 is generally constructed from similar components as the rotating control head 100, as shown in FIG. 1. Therefore, for convenience, similar components that function in the same manner will be labeled with the same numbers as the rotating control head 100. The primary difference between rotating control head 900 and rotating control head 100 is the use of two passive seal assemblies 110, an alternative cooling system using one fluid to cool the radial seals and bearings in combination with a radial seal pressure protection system, and a secondary piston SP in addition to a primary piston P for urging the piston P to the unlatched position. These differences will be discussed below in detail.
While FIG. 9 shows the rotating control head 900 latched in a housing H above a diverter D, it is contemplated that the rotating control heads as shown in the figures could be positioned with any housing or riser as disclosed in U.S. Pat. Nos. 6,138,774, 6,263,982, 6,470,975, 7,159,669 or 7,487,837, all of which are assigned to the assignee of the present invention and incorporated herein by reference for all purposes.
As shown in FIG. 9, both passive seal assemblies 110 are operably attached to the inner member support housing 135, thereby allowing the passive seal assemblies to rotate together. The passive seal assemblies are constructed and arranged in an axially-downward conical shape, thereby allowing the wellbore pressure P2 in the rotating control head 900 to act against the tapered surfaces 195 to close the passive seal assemblies around the tubular T. Additionally, the passive seal assemblies include inner diameters which are smaller than the outer diameter of the tubular T to allow an interference fit between the tubular and the passive seal assemblies.
FIG. 11 discloses a cooling system where air enters a passageway, formed as a labyrinth L, in a rotating control head RCH similar to the passageway shown in FIGS. 2A and 2B of the present invention.
FIG. 12 discloses a cooling system where hydraulic fluid moving through inlet I to outlet O is used to cool the top radial seals S1 and S2 with a seal carrier in a rotating control head RCH.
Turning now to FIGS. 9, 13 and 14, the rotating control head 900 is cooled by a heat exchanger, generally indicated at 905. As best shown in FIGS. 13 and 14, heat exchanger 905 is constructed and arranged to remove heat from the rotating control head 900 using a fluid, such as an unctuous combustible substance. One such unctuous combustible substance is a hydraulic oil, such as Mobil 630 ISO 90 weight oil. This fluid is introduced at a low temperature into inlet 965, thereafter transferring heat from upper top radial seal 975A and lower top radial seal 975B, via seal carrier 982A and its thermal transfer surfaces 982A′ and a plurality of bearings, including bearings 955, to the fluid as the fluid passes through the heat exchanger 905 and, as best shown in FIG. 14, to outlet 970.
In particular, the top radial seals 975A and 975B are cooled by circulating the hydraulic fluid, preferably oil, in and out of the bearing section B and making multiple passes around the seals 975A and 975B through a continuous spiral slot 980C in the seal housing 982B, as best shown in FIGS. 9, 13 and 14. Since the hydraulic fluid that passes through slot passageway or slot 980C is the same fluid used to pressure the bearing section B, the fluid can be circulated close to and with the radial seals 975A and 975B to improve the heat transfer properties. Although the illustrated embodiment uses a continuous spiral slot, other embodiments are contemplated for different methods for making multiple passes with one fluid adjacent to and in fluid contact with the radial seals.
As best shown in FIG. 14, the passageway of the heat exchanger 905 includes inlet passageway 980A, outlet passageway 980B, and slot passageway 980C that spirals between the lower portion of inlet passageway 980A to upper outlet passageway 980B. These multiple passes adjacent the radial seals 975A and 975B maximize the surface area covered by the heat exchanger 905. The temperature hydraulic oil entering the inlet 965 flows through the passageway in the direction illustrated by arrows 985. As the oil circulates through the passageway, the oil increases in temperature as the heat from the rotating control head 900 is transferred to the oil. The higher temperature oil exits the outlet 970. In this manner, the heat generated about the top radial seals in the rotating control head 900 is transferred to the oil passing through the multiple pass heat exchanger 905. Moreover, separate fluids are not used to cool and to lubricate the rotating control head 900. Instead, only one fluid, such as a Mobil 630 ISO fluid 90 weight oil, is used to both cool and lubricate the rotating control head 900.
Returning to FIG. 9, it is contemplated that a similar cooling system using the multiple pass heat exchanger of the present invention could be used to cool the bottom radial seals 975C and 975D of the rotating control head 900.
Returning now to FIG. 13, the top radial seals 975A and 975B are staged in tandem or series. The lower top radial seal 975B, which would be closer to the bearings 955, is a high flow seal that would allow approximately two gallons of oil per minute to pass by seal 975B. The upper top radial seal 975A, which would be the seal closer to the atmosphere or environment, would be a low flow seal that would allow approximately 1 cc of oil per hour to pass by the seal 975A. A port 984, accessible from the atmosphere, is formed between the radial seals 975A and 975B. As illustrated in both FIGS. 13 and 15B, an electronically-controlled valve, generally indicated at V200, would regulate the pressure between the radial seals 975A and 975B. Preferably, as discussed below in detail, the pressure on upper top radial seal 975A is approximately half the pressure on lower top radial seal 975B so that the differential pressure on each radial seal is lower, which in turn reduces the PV factor by approximately half. Testing of a Weatherford model 7800 rotating control head has shown that when using a Kalsi seal, with part number 381-6-11, for the upper top radial seal 975A, and a modified (as discussed below) Kalsi seal, with part number 432-32-10CCW (cutting and gluing), for the lower top radial seal 975B, has shown increased seal life of the top radial seals.
The Kalsi seals referred to herein can be obtained from Kalsi Engineering, Inc. of Sugar Land, Tex. The preferred Kalsi 381-6-11 seal is stated by Kalsi Engineering, Inc. to have a nominal inside diameter of 10�″, a seal radial depth of 0.415″�0.008″, a seal axial width of 0.300″, a gland depth of 0.380″, a gland width of 0.342″ and an approximate as-molded seal inside diameter of 10.500″ (266.7 mm). This seal is further stated by Kalsi to be fabricated from HSN (peroxide cured, high ACN) with a material hardness of Shore A durometer of 85 to 90. While the preferred Kalsi 432-32-10CCW seal is stated by Kalsi Engineering, Inc. to have a nominal inside diameter of 42.375″, a seal radial depth of 0.460″�0.007″, a seal axial width of 0.300″, a gland width of 0.342″ and an approximate as-molded seal inside diameter of 42.375″ (1,076 mm), this high flow seal was reduced to an inside diameter the same as the preferred Kalsi 381-6-11 seal, i.e. 10�″. This high flow seal 975B is further stated by Kalsi to be fabricated from HSN (fully saturated peroxide cured, medium-high ACN) with a material hardness of Shore A durometer of 85�5. It is contemplated that other similar sizes and types of manufacturers' seals, such as seals provided by Parker Hannifin of Cleveland, Ohio, could be used.
Turning now to FIGS. 15A to 25 along with below Tables 1 and 2, the startup operation of the hydraulic or fluid control of the rotating control head 900 is described. Referring particularly to FIG. 25, to start the power unit, button PB10 on the control console, generally indicated at CC, is pressed and switch SW10 is moved to the ON position. As discussed in the flowcharts of FIGS. 16-17, the program of the programmable logic controller PLC checks to make sure that button PB10 and switch SW10 were operated less than 3 seconds of each other. If the elapsed time is equal to or over 3 seconds, the change in position of SW10 is not recognized. Continuing on the flowchart of FIG. 16, the two temperature switches TS10 and TS20, also shown in FIG. 15B, are then checked. These temperature switches indicate oil tank temperature. When the oil temperature is below a designated temperature, e.g. 80� F., the heater HT10 (FIG. 15B) is turned on and the power unit will not be allowed to start until the oil temperature reaches the designated temperature. When the oil temperature is above a designated temperature, e.g. 130� F., the heater is turned off and cooler motor M2 is turned on. As described in the flowchart of FIG. 17, the last start up sequence is to check to see if the cooler motor M2 needs to be turned on.
Continuing on the flowchart of FIG. 16, the wellbore pressure P2 is checked to see if below 50 psi. As shown in below Table 2, associated alarms 10, 20, 30 and 40, light LT100 on control console CC, horn HN10 in FIG. 15B, and corresponding text messages on display monitor DM on console CC will be activated as appropriate. Wellbore pressure P2 is measured by pressure transducer PT70 (FIG. 15A). Further, reviewing FIGS. 15B to 17, when the power unit for the rotating control head, such as a Weatherford model 7800, is started, the three oil tank level switches LS10, LS20 and LS30 are checked. The level switches are positioned to indicate when the tank 634 is overfull (no room for heat expansion of the oil), when the tank is low (oil heater coil is close to being exposed), or when the tank is empty (oil heater coil is exposed). As long as the tank 634 is not overfull or empty, the power unit will pass this check by the PLC program.
Assuming that the power unit is within the above parameters, valves V80 and V90 are placed in their open positions, as shown in FIG. 15B. These valve openings unload gear pumps P2 and P3, respectively, so that when motor M1 starts, the oil is bypassed to tank 634. Valve V150 is also placed in its open position, as shown in FIG. 15A, so that any other fluid in the system can circulate back to tank 634. Returning to FIG. 15B, pump P1, which is powered by motor M1, will compensate to a predetermined value. The pressure recommended by the pump manufacturer for internal pump lubrication is approximately 300 psi. The compensation of the pump P1 is controlled by valve V10 (FIG. 15B).
Continuing review of the flowchart of FIG. 16, fluid level readings outside of the allowed values will activate alarms 50, 60 or 70 (see also below Table 2 for alarms) and their respective lights LT100, LT50 and LT60. Text messages corresponding to these alarms are displayed on display monitor DM.
When the PLC program has checked all of the above parameters the power unit will be allowed to start. Referring to the control console CC in FIG. 25, the light LT10 is then turned on to indicate the PUMP ON status of the power unit. Pressure gauge PG20 on console CC continues to read the pump pressure provided by pressure transducer PT10, shown in FIG. 15B.
When shutdown of the unit desired, the PLC program checks to see if conditions are acceptable to turn the power unit off. For example, the wellbore pressure P2 should be below 50 psi. Both the enable button PB10 must be pressed and the power switch SW10 must be turned to the OFF position within 3 seconds to turn the power unit off.
Latching Operation System Circuit
Closing the Latching System
Focusing now on FIGS. 9, 15A, 18A, 18B, 23 and 24, the retainer member LP of the latching system of housing H is closed or latched, as shown in FIG. 9, by valve V60 (FIG. 15A) changing to a flow position, so that the ports P-A, B-T are connected. The fluid pilot valve V110 (FIG. 15A) opens so that the fluid on that side of the primary piston P can go back to tank 634 via line FM40L through the B-T port. Valve V100 prevents reverse flow in case of a loss of pressure. Accumulator A (which allows room for heat expansion of the fluid in the latch assembly) is set at 900 psi, slightly above the latch pressure 800 psi, so that it will not charge. Fluid pilot valve V140 (FIG. 15A) opens so that fluid underneath the secondary piston SP goes back to tank 634 via line FM50L and valve V130 is forced closed by the resulting fluid pressure. Valve V70 is shown in FIG. 15A in its center position where all ports (APBT blocked) are blocked to block flow in any line. The pump P1, shown in FIG. 15B, compensates to a predetermined pressure of approximately 800 psi.
The retainer member LP, primary piston P and secondary piston SP of the latching system are mechanically illustrated in FIG. 9 (latching system is in its closed or latched position), schematically shown in FIG. 15A, and their operations are described in the flowcharts in FIGS. 18A, 18B, 23 and 24. Alternative latching systems are disclosed in FIGS. 1 and 8 and in U.S. Pat. No. 7,487,837.
With the above described startup operation achieved, the hydraulics switch SW20 on the control console CC is turned to the ON position. This allows the pump P1 to compensate to the required pressure later in the PLC program. The bearing latch switch SW40 on console CC is then turned to the CLOSED position. The program then follows the process outlined in the CLOSED leg of SW40 described in the flowcharts of FIGS. 18A and 18B. The pump P1 adjusts to provide 800 psi and the valve positions are then set as detailed above. As discussed below, the PLC program then compares the amount of fluid that flows through flow meters FM30, FM40 and FM50 to ensure that the required amount of fluid to close or latch the latching system goes through the flow meters. Lights LT20, LT30, LT60 and LT70 on console CC show the proper state of the latch. Pressure gauge PG20, as shown on the control console CC, continues to read the pressure from pressure transducer PT10 (FIG. 15B).
Primary Latching System Opening
Similar to the above latch closing process, the PLC program follows the OPEN leg of SW40 as discussed in the flowchart of FIG. 18A and then the OFF leg of SW50 of FIG. 18A to open or unlatch the latching system. Turning to FIG. 15A, prior to opening or unlatching the retainer member LP of the latching system, pressure transducer PT70 checks the wellbore pressure P2. If the PT70 reading is above a predetermined pressure (approximately 50 psi), the power unit will not allow the retainer member LP to open or unlatch. Three-way valve V70 (FIG. 15A) is again in the APBT blocked position. Valve V60 shifts to flow position P-B and A-T. The fluid flows through valve V110 into the chamber to urge the primary piston P to move to allow retainer member LP to unlatch. The pump P1, shown in FIG. 15B, compensates to a predetermined value (approximately 2000 psi). Fluid pilots open valve V100 to allow fluid of the primary piston P to flow through line FM30L and the A-T ports back to tank 634.
Secondary Latching System Opening
The PLC program following the OPEN leg of SW40 and the OPEN leg of SW50, described in the flowchart of FIG. 18A, moves the secondary piston SP. The secondary piston SP is used to open or unlatch the primary piston P and, therefore, the retainer member LP of the latching system. Prior to unlatching the latching system, pressure transducer PT70 again checks the wellbore pressure P2. If PT70 is reading above a predetermined pressure (approximately 50 psi), the power unit will not allow the latching system to open or unlatch. Valve V60 is in the APBT blocked position, as shown in FIG. 15A. Valve V70 then shifts to flow position P-A and B-T. Fluid flows to the chamber of the secondary latch piston SP via line FM50L. With valve V140 forced closed by the resulting pressure and valve V130 piloted open, fluid from both sides of the primary piston P is allowed to go back to tank 634 though the B-T ports of valve V70.
Bearing Assembly Circuit
Continuing to review FIGS. 9, 15A, 15B, 18A and 18B and the below Tables 1 and 2, now review FIGS. 19 to 22 describing the bearing assembly circuit.
Valve positions on valve V80 and valve V90, shown in FIG. 15B, and valve V160, shown in FIG. 15A, are moved to provide a pressure in the rotating control head that is above the wellbore pressure P2. In particular, the wellbore pressure P2 is measured by pressure transducer PT70, shown in FIG. 15A. Depending on the wellbore pressure P2, valve V90 and valve V80 (FIG. 15B) are either open or closed. By opening either valve, pressure in the rotating control head can be reduced by allowing fluid to go back to tank 634. Also, depending on pressure in the rotating control head, valve V160 wig move to a position that selects a different size orifice. The orifice size, e.g. 3/32″ or ⅛″ (FIG. 15A), will determine how much back pressure is in the rotating control head. By using this combination of valves V80, V90 and V160, four different pressures can be achieved.
During the operation of the bearing assembly circuit, the temperature switches TS10 and TS20, described in the above startup operation, continue to read the oil temperature in the tank 634, and operate the heater HT10 or cooler motor M2, as required. For example, if the oil temperature exceeds a predetermined value, the cooler motor M2 is turned on and the cooler will transfer heat from the oil returning from the bearing section or assembly B.
Flow meter FM10 measures the volume or flow rate of fluid or oil to the chamber in the bearing section or assembly B via line FM10L. Flow meter FM20 measures the volume or flow rate of fluid or oil from the chamber in the bearing section or assembly B via line FM20L. As discussed further below in the bearing leak detection system section, if the flow meter FM20 reading is greater than the flow meter FM10 reading, this could indicate that wellbore fluid is entering the bearing assembly chamber. Valve V150 is then moved from the open position, as shown in FIG. 15A, to its closed position to keep the wellbore fluid from going back to tank 634.
Regulating Pressure in the Radial Seals
Reviewing FIGS. 13, 14, 15B, 22 and 23 along with the below Tables 1 and 2, pressure transducer PT80 (FIG. 15B) reads the amount of fluid “seal bleed” pressure between the top radial seals 975A and 975B via port 984. As discussed above, proportional relief valve V200 adjusts to maintain a predetermined pressure between the two radial seals 975A and 975B. Based on the well pressure P2 indicated by the pressure transducer PT70, the valve V200 adjusts to achieve the desired “seal bleed” pressure as shown in the below Table 1.
SEAL BLEED PRESSURE
1200-UP
The flowcharts of FIGS. 18A and 18B on the CLOSED leg of SW40 and after the subroutine to compare flow meters FM30, FM40 and FM50, describes how the valves adjust to match the pressures in above Table 1. FIGS. 19 to 22 describes a subroutine for the program to adjust pressures in relation to the wellbore pressure P2.
During the running of the PLC program, certain sensors such as flow meters and pressure transducers are checked. If the values are out of tolerance, alarms are activated. The flowcharts of FIGS. 16, 17, 18A and 18B. describe when the alarms are activated. Below Table 2 shows the lights, horn and causes associated with the activated alarms. The lights listed in Table 2 correspond to the lights shown on the control console CC of FIG. 25. As discussed below, a text message corresponding to the cause is sent to the display monitor DM on the control console CC.
Latch Leak Detection System
FM30/FM40 Comparison
Usually the PLC program will run a comparison where the secondary piston SP is “bottomed out” or in its latched position, such as shown in FIG. 9, or when only a primary piston P is used, such as shown in FIG. 1, the piston P is bottomed out. In this comparison, the flow meter FM30 coupled to the line FM30L measures either the flow volume value or flow rate value of fluid to the piston chamber to move the piston P to the latched position, as shown in FIG. 9, from the unlatched position, as shown in FIG. 1. Also, the flow meter FM40 coupled to the line FM40L measures the desired flow volume value or flow rate value from the piston chamber. Since the secondary piston SP is bottomed out, there should be no flow in line FM50L, as shown in FIG. 9. Since no secondary piston is shown in FIG. 1, there is no line FM50L or flow meter FM50.
In this comparison, if there are no significant leaks, the flow volume value or flow rate value measured by flow meter FM30 should be equal to the flow volume value or flow rate value, respectively, measured by flow meter FM40 within a predetermined tolerance. If a leak is detected because the comparison is outside the predetermined tolerance, the results of this FM30/FM40 comparison would be displayed on display monitor DM on control console CC, as shown in FIG. 25, preferably in a text message, such as “Alarm 90—Fluid Leak”. Furthermore, if the values from flow meter FM30 and flow meter FM40 are not within the predetermined tolerance, i.e. a leak is detected, the corresponding light LT100 would be displayed on the control console CC.
FM30/FM50 Comparison
In a less common comparison, the secondary piston SP would be in its “full up” position. That is, the secondary piston SP has urged the primary piston P, when viewing FIG. 9, as far up as it can move to its full unlatched position. In this comparison, the flow volume value or flow rate value, measured by flow meter FM30 coupled to line FM30L, to move piston P to its latched position, as shown in FIG. 9, is measured. If the secondary piston SP is sized so that it would block line FM40L, no fluid would be measured by flow meter FM40. But fluid beneath the secondary piston SP would be evacuated via line FM50L from the piston chamber of the latch assembly. Flow meter 50 would then measure the flow volume value or flow rate value. The measured flow volume value or flow rate value from flow meter FM30 is then compared to the measured flow volume value or flow rate value from flow meter FM50.
If the compared FM30/FM50 values are within a predetermined tolerance, then no significant leaks are considered detected. If a leak is detected, the results of this FM30/FM50 comparison would be displayed on display monitor DM on control console CC, preferably in a text message, such as “Alarm 100—Fluid Leak”. Furthermore, if the values from flow meter FM30 and flow meter FM50 are not within a predetermined tolerance, the corresponding light LT100 would be displayed on the control console CC.
FM30/FM40+FM50 Comparison
Sometimes the primary piston P is in its full unlatched position and the secondary piston SP is somewhere between its bottomed out position and in contact with the fully unlatched piston P. In this comparison, the flow volume value or flow rate value measured by the flow meter FM30 to move piston P to its latched position is measured. If the secondary piston SP is sized so that it does not block line FM40L, fluid between secondary piston SP and piston P is evacuated by line FM40L. The flow meter FM40 then measures the flow volume value or flow rate value via line FM40L. This measured value from flow meter FM40 is compared to the measured value from flow meter FM30. Also, the flow value beneath secondary piston SP is evacuated via line FM50L and measured by flow meter FM50.
If the flow value from flow meter FM30 is not within a predetermined tolerance of the compared sum of the flow values from flow meter FM40 and flow meter FM50, then the corresponding light LT100 would be displayed on the control console CC. This detected leak is displayed on display monitor DM in a text message.
Measured Value/Predetermined Value
An alternative to the above leak detection methods of comparing measured values is to use a predetermined or previously calculated value. The PLC program then compares the measured flow value in and/or from the latching system to the predetermined flow value plus a predetermined tolerance.
It is noted that in addition to indicating the latch position, the flow meters FM30, FM40 and FM50 are also monitored so that if fluid flow continues after the piston P has moved to the closed or latched position for a predetermined time period, a possible hose or seal leak is flagged.
For example, alarms 90, 100 and 110, as shown in below Table 2, could be activated as follows:
Alarm 90—primary piston P is in the open or unlatched position. The flow meter FM40 measured flow value is compared to a predetermined value plus a tolerance to indicate the position of piston P. When the flow meter FM40 reaches the tolerance range of this predetermined value, the piston P is indicated in the open or unlatched position. If the flow meter FM40 either exceeds this tolerance range of the predetermined value or continues to read a flow value after a predetermined time period, such as an hour, the PLC program indicates the alarm 90 and its corresponding light and text message as discussed herein.
Alarm 100—secondary piston SP is in the open or unlatched position. The flow meter FM50 measured flow value is compared to a predetermined value plus a tolerance to indicate the position of secondary piston SP. When the flow meter FM50 reaches the tolerance range of this predetermined value, the secondary piston SP is indicated in the open or unlatched position. If the flow meter FM50 either exceeds this tolerance range of the predetermined value or continues to read a flow value after a predetermined time period, such as an hour, the PLC program indicates the alarm 100 and its corresponding light and text message as discussed herein.
Alarm 110—primary piston P is in the closed or latched position. The flow meter FM30 measured flow value is compared to a predetermined value plus a tolerance to indicate the position of primary piston P. When the flow meter FM30 reaches the tolerance range of this predetermined value, the primary piston P is indicated in the closed or latched position. If the flow meter FM30 either exceeds this tolerance range of the predetermined value or continues to read a flow value after a predetermined time period, such as an hour, the PLC program indicates the alarm 110 and its corresponding light and text message as discussed herein.
Bearing Leak Detection System
FM10/FM20 Comparison
A leak detection system can also be used to determine if the bearing section or assembly B is losing fluid, such as oil, or, as discussed above, gaining fluid, such as wellbore fluids. As shown in FIG. 15A, line FM10L and line FM20L move fluid to and from the bearing assembly B of a rotating control head and are coupled to respective flow meters FM10 and FM20.
If the measured fluid value, such as fluid volume value or fluid rate value, from flow meter FM10 is not within a predetermined tolerance of the measured fluid value from flow meter FM20, then alarms 120, 130 or 140, as described below in Table 2, are activated. For example, if the measured flow value to the bearing assembly B is greater than the measured flow value from the bearing assembly plus a predetermined percentage tolerance, then alarm 120 is activated and light LT90 on control console CC is turned ion. Also, a text message is displayed on display monitor DM on the control console CC, such as “Alarm 120—Losing Oil.” For example, this loss could be from the top radial seals leaking oil to the atmosphere, or the bottom radial seals leaking oil down the wellbore.
If the measured flow value from the bearing assembly read by flow meter FM20 is greater than the measured flow value to the bearing assembly read by flow meter FM10 plus a predetermined percentage tolerance, then alarm 130 is activated, light LT90 is turned on and a text message such as “Alarm 130—Gaining Oil” is displayed on display monitor DM.
If the measured flow meter FM20 flow value/measured flow meter FM10 flow value is higher than the alarm 130 predetermined percentage tolerance, then alarm 140 is activated, light LT90 is turned on and a horn sounds in addition to a text message on display monitor DM, such as “Alarm 140—Gaining Oil.”
An alternative to the above leak detection methods of comparing measured values is to use a predetermined or previously calculated value. The PLC program then compares the measured flow value in and/or from the bearing assembly B to the predetermined flow value plus a predetermined tolerance.
TABLE 2 ALARM # LIGHT HORN CAUSE 10 LT100 WB >100 WELLBORE > 50, PT10 = 0; NO LATCH PUMP PRESSURE 20 LT100 WB >100 WELLBORE > 50, PT20 = 0; NO BEARING LUBE PRESSURE 30 LT100 Y WELLBORE > 50, LT20 = OFF; LATCH NOT CLOSED 40 LT100 Y WELLBORE > 50, LT30 = OFF; SECONDARY LATCH NOT CLOSED 50 LT100 LS30 = ON; TANK OVERFULL 60 LT50 LS20 = OFF; TANK LOW 70 LT50 Y LS10 = OFF; TANK EMPTY 80 LT100 Y WELLBORE > 100, PT10 = 0; NO LATCH PRESSURE 90 LT100 FM40; FLUID LEAK; 10% TOLERANCE + FLUID MEASURE 100 LT100 FM50; FLUID LEAK; 10% TOLERANCE + FLUID MEASURE 110 LT100 FM30; FLUID LEAK; 10% TOLERANCE + FLUID MEASURE 120 LT90 FM10 > FM20 + 25%; BEARING LEAK (LOSING OIL) 130 LT90 FM20 > FM10 + 15%; BEARING LEAK (GAINING OIL) 140 LT90 Y FM20 > FM10 + 30%; BEARING LEAK (GAINING OIL) Piston Position Indicators
Additional methods are contemplated to indicate position of the primary piston P and/or secondary piston SP in the latching system. One example would be to use an electrical sensor, such as a linear displacement transducer, to measure the distance the selected piston has moved.
Another method could be drilling the housing of the latch assembly for a valve that would be opened or closed by either the primary piston P, as shown in the embodiment of FIG. 1, or the secondary piston SP, as shown in the embodiment of FIGS. 9, 26 and 27. In this method, a port PO would be drilled or formed in the bottom of the piston chamber of the latch assembly. Port PO is in fluid communication with an inlet port IN (FIG. 26) and an outlet port OU (FIG. 27) extending perpendicular (radially outward) from the piston chamber of the latch assembly. These perpendicular ports would communicate with respective passages INP and OUP that extend upward in the radially outward portion of the latch assembly housing. Housing passage OUP is connected by a hose to a pressure transducer and/or flow meter. A machined valve seat VS in the port to the piston chamber receives a corresponding valve seat, such as a needle valve seat. The needle valve seat would be fixedly connected to a rod R receiving a coil spring CS about its lower portion to urge the needle valve seat to the open or unlatched position if neither primary piston P (FIG. 1 embodiment) nor secondary piston SP (FIGS. 9, 26 and 27 embodiments) moves the needle valve seat to the closed or latched position. An alignment retainer member AR is sealed as the member is threadably connected to the housing H. The upper portion of rod R is slidably sealed with retainer member AR.
If a flow value and/or pressure is detected in the respective flow meter and/or pressure transducer communicating with passage OUP, then the valve is indicated open. This open valve indicates the piston is in the open or unlatched position. If no flow value and/or pressure is detected in the respective flow meter and/or pressure transducer communicating with passage OUP, then the valve is indicated closed. This closed valve indicates the piston is in the closed or latched position. The above piston position would be shown on the console CC, as shown in FIG. 25, by lights LT20 or LT60 and LT30 or LT70 along with a corresponding text message on display monitor DM.
Patent CitationsCited PatentFiling datePublication dateApplicantTitleUS282073Jul 31, 1883 Electric ore-separatorUS517509Dec 15, 1893Apr 3, 1894 Stuffing-boxUS1157644Jul 24, 1911Oct 19, 1915Terry Steam Turbine CompanyVertical bearing.US1472952Feb 13, 1922Nov 6, 1923Longyear E J CoOil-saving device for oil wellsUS1503476May 24, 1921Aug 5, 1924Hughes Tool CoApparatus for well drillingUS1528560Oct 20, 1923Mar 3, 1925Herbert SchmidtPacking toolUS1546467Jan 9, 1924Jul 21, 1925Bennett Joseph FOil or gas drilling mechanismUS1560763Jan 27, 1925Nov 10, 1925Collins Frank MPacking head and blow-out preventer for rotary-type well-drilling apparatusUS1700894Aug 18, 1924Feb 5, 1929JoyceMetallic packing for alpha fluid under pressureUS1708316Sep 9, 1926Apr 9, 1929Macclatchie John WBlow-out preventerUS1769921Dec 11, 1928Jul 8, 1930Ingersoll Rand CoCentralizer for drill steelsUS1776797Aug 15, 1928Sep 30, 1930Waldo SheldonPacking for rotary well drillingUS1813402Jun 1, 1927Jul 7, 1931Hewitt Evert NPressure drilling headUS1831956Oct 27, 1930Nov 17, 1931Reed Roller Bit CoBlow out preventerUS1836470Feb 24, 1930Dec 15, 1931Humason Granville ABlow-out preventerUS1902906Sep 3, 1931Mar 28, 1933Cecil Seamark Lewis MervynCasing head equipmentUS1942366Sep 20, 1930Jan 2, 1934Cecil Seamark Lewis MervynCasing head equipmentUS2036537Jul 22, 1935Apr 7, 1936Otis Herbert CKelly stuffing boxUS2038140Jul 6, 1931Apr 21, 1936Hydril CoPacking headUS2071197May 7, 1934Feb 16, 1937Erwin BurnsBlow-out preventerUS2124015Nov 19, 1935Jul 19, 1938Hydril CoPacking headUS2126007Apr 12, 1937Aug 9, 1938Guiberson CorpDrilling headUS2144682Aug 12, 1936Jan 24, 1939Macclatchie Mfg CompanyBlow-out preventerUS2148844Oct 2, 1936Feb 28, 1939Hydril CoPacking head for oil wellsUS2163813Aug 24, 1936Jun 27, 1939Hydril CoOil well packing headUS2165410May 24, 1937Jul 11, 1939Penick Arthur JBlowout preventerUS2170915Aug 9, 1937Aug 29, 1939Schweitzer Frank JCollar passing pressure stripperUS2170916May 9, 1938Aug 29, 1939Schweitzer Frank JRotary collar passing blow-out preventer and stripperUS2175648Jan 18, 1937Oct 10, 1939Roach Edmund JBlow-out preventer for casing headsUS2176355Sep 2, 1937Oct 17, 1939 Drumng headUS2185822Nov 6, 1937Jan 2, 1940Nat Supply CoRotary swivelUS2199735Dec 29, 1938May 7, 1940Fred G BeckmanPacking glandUS2211122Mar 10, 1938Aug 13, 1940J H Mcevoy & CompanyTubing head and hangerUS2222082Dec 1, 1938Nov 19, 1940Nat Supply CoRotary drilling headUS2233041Sep 14, 1939Feb 25, 1941Arthur J PenickBlowout preventerUS2243340May 23, 1938May 27, 1941Hild Frederic WRotary blowout preventerUS2243439Jan 18, 1938May 27, 1941Guiberson CorpPressure drilling headUS2287205Jan 27, 1939Jun 23, 1942Hydril Company Of CaliforniaPacking headUS2303090Nov 8, 1938Nov 24, 1942Guiberson CorpPressure drilling headUS2313169May 9, 1940Mar 9, 1943Penick Arthur JWell head assemblyUS2325556Mar 22, 1941Jul 27, 1943Guiberson CorpWell swabUS2338093Jun 28, 1941Jan 4, 1944George E Failing Supply CompanKelly rod and drive bushing thereforUS2480955Oct 29, 1945Sep 6, 1949Oil Ct Tool CompanyJoint sealing means for well headsUS2506538Feb 24, 1947May 2, 1950 Means for protecting well drillingUS2529744May 18, 1946Nov 14, 1950Schweitzer Frank JChoking collar blowout preventer and stripperUS2609836Aug 16, 1946Sep 9, 1952Hydril CorpControl head and blow-out preventerUS2628852Feb 2, 1949Feb 17, 1953Crane Packing CoCooling system for double sealsUS2646999Jan 19, 1949Jul 28, 1953Filton LtdFluid sealUS2649318May 18, 1950Aug 18, 1953Blaw Knox CoPressure lubricating systemUS2731281Aug 19, 1950Jan 17, 1956Hydril CorpKelly packer and blowout preventerUS2746781Jan 26, 1952May 22, 1956Petroleum Mechanical Dev CorpWiping and sealing devices for well pipesUS2760750Aug 13, 1953Aug 28, 1956Shaffer Tool WorksStationary blowout preventerUS2760795Jun 15, 1953Aug 28, 1956Shaffer Tool WorksRotary blowout preventer for well apparatusUS2764999Aug 29, 1952Oct 2, 1956British Messier LtdHydraulic accumulatorsUS2808229Nov 12, 1954Oct 1, 1957Continental Oil CoOff-shore drillingUS2808230Jan 17, 1955Oct 1, 1957Continental Oil CoOff-shore drillingUS2846178Jan 24, 1955Aug 5, 1958Regan Forge & Eng CoConical-type blowout preventerUS2846247Nov 23, 1953Aug 5, 1958Guiberson CorpDrilling headUS2853274Jan 3, 1955Sep 23, 1958Collins Henry HRotary table and pressure fluid seal thereforUS2862735May 23, 1955Dec 2, 1958Hydril CoKelly packer and blowout preventerUS2886350Apr 22, 1957May 12, 1959Horne Robert JacksonCentrifugal sealsUS2904357Mar 10, 1958Sep 15, 1959Hydril CoRotatable well pressure sealUS2927774May 10, 1957Mar 8, 1960Phillips Petroleum CoRotary sealUS2929610Dec 27, 1954Mar 22, 1960Continental Oil CoDrillingUS2962096Oct 22, 1957Nov 29, 1960Hydril CoWell head connectorUS2995196Jul 8, 1957Aug 8, 1961Shaffer Tool WorksDrilling headUS3023012Jun 9, 1959Feb 27, 1962Shaffer Tool WorksSubmarine drilling head and blowout preventerUS3029083Feb 4, 1958Apr 10, 1962Shaffer Tool WorksSeal for drilling heads and the likeUS3032125Jul 10, 1957May 1, 1962Jersey Prod Res CoOffshore apparatusUS3033011Aug 31, 1960May 8, 1962Drilco Oil Tools IncResilient rotary drive fluid conduit connectionUS3052300Feb 6, 1959Sep 4, 1962Hampton Donald MWell head for air drilling apparatusUS3096999Jul 7, 1958Jul 9, 1963Cameron Iron Works IncPipe joint having remote control coupling meansUS3100015Oct 5, 1959Aug 6, 1963Regan Forge & Eng CoMethod of and apparatus for running equipment into and out of wellsUS3128614Oct 27, 1961Apr 14, 1964Grant Oil Tool CompanyDrilling headUS3134613Mar 31, 1961May 26, 1964Regan Forge & Eng CoQuick-connect fitting for oil well tubingUS3176996Oct 12, 1962Apr 6, 1965Barnett Leon TrumanOil balanced shaft sealUS3203358Aug 13, 1962Aug 31, 1965Regan Forge & Eng CoFluid flow control apparatusUS3209829May 8, 1961Oct 5, 1965Shell Oil CoWellhead assembly for under-water wellsUS3216731Feb 12, 1962Nov 9, 1965Otis Eng CoWell toolsUS3225831Apr 16, 1962Dec 28, 1965Hydril CoApparatus and method for packing off multiple tubing stringsUS3259198May 28, 1963Jul 5, 1966Shell Oil CoMethod and apparatus for drilling underwater wellsUS3268233Oct 7, 1963Aug 23, 1966Brown Oil ToolsRotary stripper for well pipe stringsUS3285352Dec 3, 1964Nov 15, 1966Hunter Joseph MRotary air drilling headUS3288472Jul 1, 1963Nov 29, 1966Regan Forge & Eng CoMetal sealUS3289761Apr 15, 1964Dec 6, 1966Smith Robbie JMethod and means for sealing wellsUS3294112Jul 1, 1963Dec 27, 1966Regan Forge & Eng CoRemotely operable fluid flow control valveUS3302048Sep 23, 1965Jan 31, 1967Barden CorpSelf-aligning gas bearingUS3313345Jun 2, 1964Apr 11, 1967Chevron ResMethod and apparatus for offshore drilling and well completionUS3313358Apr 1, 1964Apr 11, 1967Chevron ResConductor casing for offshore drilling and well completionUS3323773Feb 1, 1963Jun 6, 1967Shaffer Tool WorksBlow-out preventerUS3333870Dec 30, 1965Aug 1, 1967Regan Forge & Eng CoMarine conductor coupling with double seal constructionUS3347567Nov 29, 1963Oct 17, 1967Regan Forge & Eng CoDouble tapered guidance apparatusUS3360048Jun 29, 1964Dec 26, 1967Regan Forge & Eng CoAnnulus valveUS3372761Jun 30, 1965Mar 12, 1968Gils Adrianus Wilhelmus VanMaximum allowable back pressure controller for a drilled holeUS3387851Jan 12, 1966Jun 11, 1968Shaffer Tool WorksTandem stripper sealing apparatusUS3397928Nov 8, 1965Aug 20, 1968Edward M. GalleSeal means for drill bit bearingsUS3400938Sep 16, 1966Sep 10, 1968Bob WilliamsDrilling head assemblyUS3401600Dec 23, 1965Sep 17, 1968Bell Aerospace CorpControl system having a plurality of control chains each of which may be disabled in event of failure thereofUS3405763Feb 18, 1966Oct 15, 1968Gray Tool CoWell completion apparatus and methodUS3421580Aug 15, 1966Jan 14, 1969Rockwell Mfg CoUnderwater well completion method and apparatusUS3443643Dec 30, 1966May 13, 1969Cameron Iron Works IncApparatus for controlling the pressure in a wellUS3445126May 19, 1966May 20, 1969Regan Forge & Eng CoMarine conductor couplingUS3452815Jul 31, 1967Jul 1, 1969Regan Forge & Eng CoLatching mechanismUS3472518Oct 24, 1966Oct 14, 1969Texaco IncDynamic seal for drill pipe annulusUS3476195Nov 15, 1968Nov 4, 1969Hughes Tool CoLubricant relief valve for rock bitsUS3481610Jun 2, 1967Dec 2, 1969Bowen Tools IncSeal valve assemblyUS3485051May 22, 1967Dec 23, 1969Regan Forge & Eng CoDouble tapered guidance methodUS3492007Jun 7, 1967Jan 27, 1970Regan Forge & Eng CoLoad balancing full opening and rotating blowout preventer apparatusUS3493043Aug 9, 1967Feb 3, 1970Regan Forge & Eng CoMono guide line apparatus and methodUS3503460Jul 3, 1968Mar 31, 1970Byron Jackson IncPipe handling and centering apparatus for well drilling rigsUS3522709Feb 19, 1968Aug 4, 1970Metalliques Cie Franc EntrepriMarine platform structureUS3529835May 15, 1969Sep 22, 1970Hydril CoKelly packer and lubricatorUS3561723May 7, 1968Feb 9, 1971Cugini Edward TStripping and blow-out preventer deviceUS3583480 *Jun 10, 1970Jun 8, 1971Regan Forge & Eng CoMethod of providing a removable packing insert in a subsea stationary blowout preventer apparatusUS3587734Sep 8, 1969Jun 28, 1971Shafco Ind IncAdapter for converting a stationary blowout preventer to a rotary blowout preventerUS3603409Mar 27, 1969Sep 7, 1971Regan Forge & Eng CoMethod and apparatus for balancing subsea internal and external well pressuresUS3621912Dec 10, 1969Nov 23, 1971Exxon Production Research CoRemotely operated rotating wellheadUS3631834Jan 26, 1970Jan 4, 1972Waukesha Bearings CorpPressure-balancing oil system for stern tubes of shipsUS3638721Dec 10, 1969Feb 1, 1972Exxon Production Research CoFlexible connection for rotating blowout preventerUS3638742Jan 6, 1970Feb 1, 1972Wallace William AWell bore seal apparatus for closed fluid circulation assemblyUS3653350Dec 4, 1970Apr 4, 1972Waukesha Bearings CorpPressure balancing oil system for stern tubes of shipsUS3661409Aug 14, 1969May 9, 1972Gray Tool CoMulti-segment clampUS3664376Jan 26, 1970May 23, 1972Regan Forge & Eng CoFlow line diverter apparatusUS3667721Apr 13, 1970Jun 6, 1972Rucker CoBlowout preventerUS3677353Jul 15, 1970Jul 18, 1972Cameron Iron Works IncApparatus for controlling well pressureUS3724862Aug 26, 1971Apr 3, 1973Biffle MDrill head and sealing apparatus thereforeUS3741296Jun 14, 1971Jun 26, 1973Hydril CoReplacement of sub sea blow out preventer packing unitsUS3779313Jul 1, 1971Dec 18, 1973Regan Forge & Eng CoLe connecting apparatus for subsea wellheadUS3815673Feb 16, 1972Jun 11, 1974Exxon Production Research CoMethod and apparatus for controlling hydrostatic pressure gradient in offshore drilling operationsUS3827511Dec 18, 1972Aug 6, 1974Cameron Iron Works IncApparatus for controlling well pressureUS3847215Aug 13, 1973Nov 12, 1974Mcevoy Oilfield Equipment CoUnderwater well completion method and apparatusUS3868832Mar 8, 1973Mar 4, 1975Biffle Morris SRotary drilling head assemblyUS3872717Jan 3, 1972Mar 25, 1975Fox Nathaniel SSoil testing method and apparatusUS3924678Jul 15, 1974Dec 9, 1975Vetco Offshore Ind IncCasing hanger and packing running apparatusUS3934887Jan 30, 1975Jan 27, 1976Dresser Industries, Inc.Rotary drilling head assemblyUS3952526Feb 3, 1975Apr 27, 1976Regan Offshore International, Inc.Flexible supportive joint for sub-sea riser flotation meansUS3955622Jun 9, 1975May 11, 1976Regan Offshore International, Inc.Dual drill string orienting apparatus and methodUS3965987Dec 19, 1974Jun 29, 1976Dresser Industries, Inc.Method of sealing the annulus between a toolstring and casing headUS3976148Sep 12, 1975Aug 24, 1976The Offshore CompanyMethod and apparatus for determining onboard a heaving vessel the flow rate of drilling fluid flowing out of a wellhole and into a telescoping marine riser connecting between the wellhouse and the vesselUS3984990Jun 9, 1975Oct 12, 1976Regan Offshore International, Inc.Support means for a well riser or the likeUS3992889Jun 9, 1975Nov 23, 1976Regan Offshore International, Inc.Flotation means for subsea well riserUS3999766Nov 28, 1975Dec 28, 1976General Electric CompanyDynamoelectric machine shaft sealUS4037890Apr 15, 1975Jul 26, 1977Hitachi, Ltd.Vertical type antifriction bearing deviceUS4046191Jul 7, 1975Sep 6, 1977Exxon Production Research CompanySubsea hydraulic chokeUS4052703May 5, 1975Oct 4, 1977Automatic Terminal Information Systems, Inc.Intelligent multiplex system for subsurface wellsUS4053023Aug 22, 1974Oct 11, 1977Mcevoy Oilfield Equipment Co.Underwater well completion method and apparatusUS4063602Nov 1, 1976Dec 20, 1977Exxon Production Research CompanyDrilling fluid diverter systemUS4087097Feb 8, 1977May 2, 1978Commissariat A L'energie AtomiqueSealing device for the emergent shaft end of a rotating machineUS4091881Apr 11, 1977May 30, 1978Exxon Production Research CompanyArtificial lift system for marine drilling riserUS4098341 *Feb 28, 1977Jul 4, 1978Hydril CompanyRotating blowout preventer apparatusUS4099583Apr 11, 1977Jul 11, 1978Exxon Production Research CompanyGas lift system for marine drilling riserUS4109712Aug 1, 1977Aug 29, 1978Regan Offshore International, Inc.Safety apparatus for automatically sealing hydraulic lines within a sub-sea well casingUS4143880Mar 23, 1978Mar 13, 1979Dresser Industries, Inc.Reverse pressure activated rotary drill head sealUS4143881Mar 23, 1978Mar 13, 1979Dresser Industries, Inc.Lubricant cooled rotary drill head sealUS4149603Sep 6, 1977Apr 17, 1979Arnold James FRiserless mud return systemUS4154448Oct 18, 1977May 15, 1979Biffle Morris SRotating blowout preventor with rigid washpipeUS4157186Oct 17, 1977Jun 5, 1979Murray Donnie LHeavy duty rotating blowout preventorUS4183562Apr 1, 1977Jan 15, 1980Regan Offshore International, Inc.Marine riser conduit section coupling meansUS4200312Feb 6, 1978Apr 29, 1980Regan Offshore International, Inc.Subsea flowline connectorUS4208056May 11, 1979Jun 17, 1980Biffle Morris SRotating blowout preventor with index kelly drive bushing and stripper rubberUS4216835Sep 5, 1978Aug 12, 1980Nelson Norman ASystem for connecting an underwater platform to an underwater floorUS4222590Feb 2, 1978Sep 16, 1980Regan Offshore International, Inc.Equally tensioned coupling apparatusUS4249600Jun 6, 1978Feb 10, 1981Brown Oil Tools, Inc.Double cylinder systemUS4281724Aug 24, 1979Aug 4, 1981Smith International, Inc.Drilling headUS4282939Jun 20, 1979Aug 11, 1981Exxon Production Research CompanyMethod and apparatus for compensating well control instrumentation for the effects of vessel heaveUS4285406Aug 24, 1979Aug 25, 1981Smith International, Inc.Drilling headUS4291772Mar 25, 1980Sep 29, 1981Standard Oil Company (Indiana)Drilling fluid bypass for marine riserUS4293047Aug 24, 1979Oct 6, 1981Smith International, Inc.Drilling headUS4304310Aug 24, 1979Dec 8, 1981Smith International, Inc.Drilling headUS4310058Apr 28, 1980Jan 12, 1982Otis Engineering CorporationWell drilling methodUS4312404May 1, 1980Jan 26, 1982Lynn International Inc.Rotating blowout preventerUS4313054Mar 31, 1980Jan 26, 1982Carrier CorporationPart load calculatorUS4326584Aug 4, 1980Apr 27, 1982Regan Offshore International, Inc.Kelly packing and stripper seal protection elementUS4335791Apr 6, 1981Jun 22, 1982Evans Robert FPressure compensator and lubricating reservoir with improved response to substantial pressure changes and adverse environmentUS4336840Dec 8, 1980Jun 29, 1982Hughes Tool CompanyDouble cylinder systemUS4337653Apr 29, 1981Jul 6, 1982Koomey, Inc.Blowout preventer control and recorder systemUS4345769Mar 16, 1981Aug 24, 1982Washington Rotating Control Heads, Inc.Drilling head assembly sealUS4349204Apr 29, 1981Sep 14, 1982Lynes, Inc.Non-extruding inflatable packer assemblyUS4353420Oct 31, 1980Oct 12, 1982Cameron Iron Works, Inc.Wellhead apparatus and method of running sameUS4355784Aug 4, 1980Oct 26, 1982Warren Automatic Tool CompanyMethod and apparatus for controlling back pressureUS4361185Oct 31, 1980Nov 30, 1982Biffle John MStripper rubber for rotating blowout preventorsUS4363357Oct 9, 1980Dec 14, 1982Hunter Joseph MRotary drilling headUS4367795Oct 31, 1980Jan 11, 1983Biffle Morris SRotating blowout preventor with improved seal assemblyUS4378849Feb 27, 1981Apr 5, 1983Wilks Joe ABlowout preventer with mechanically operated relief valveUS4383577Feb 10, 1981May 17, 1983Pruitt Alfred BRotating head for air, gas and mud drillingUS4384724Dec 23, 1980May 24, 1983Derman Karl G ESealing deviceUS4386667May 1, 1980Jun 7, 1983Hughes Tool CompanyPlunger lubricant compensator for an earth boring drill bitUS4387771Oct 14, 1980Jun 14, 1983Jones Darrell LWellhead system for exploratory wellsUS4398599Feb 23, 1981Aug 16, 1983Chickasha Rentals, Inc.Rotating blowout preventor with adaptorUS4406333Oct 13, 1981Sep 27, 1983Adams Johnie RRotating head for rotary drilling rigsUS4407375Aug 17, 1981Oct 4, 1983Tsukamoto Seiki Co., Ltd.Pressure compensator for rotary earth boring toolUS4413653Oct 8, 1981Nov 8, 1983Halliburton CompanyInflation anchorUS4416340Dec 24, 1981Nov 22, 1983Smith International, Inc.Rotary drilling headUS4423776Jun 25, 1981Jan 3, 1984Wagoner E DewayneDrilling head assemblyUS4424861Oct 8, 1981Jan 10, 1984Halliburton CompanyInflatable anchor element and packer employing sameUS4427072May 21, 1982Jan 24, 1984Armco Inc.Method and apparatus for deep underwater well drilling and completionUS4439068Sep 23, 1982Mar 27, 1984Armco Inc.Releasable guide post mount and method for recovering guide posts by remote operationsUS4440232Jul 26, 1982Apr 3, 1984Koomey, Inc.Well pressure compensation for blowout preventersUS4441551Oct 15, 1981Apr 10, 1984Biffle Morris SModified rotating head assembly for rotating blowout preventorsUS4444250Dec 13, 1982Apr 24, 1984Hydril CompanyFlow diverterUS4444401Dec 13, 1982Apr 24, 1984Hydril CompanyFlow diverter seal with respective oblong and circular openingsUS4448255 *Aug 17, 1982May 15, 1984Shaffer Donald URotary blowout preventerUS4456062Dec 13, 1982Jun 26, 1984Hydril CompanyFlow diverterUS4456063Dec 13, 1982Jun 26, 1984Hydril CompanyFlow diverterUS4457489Jul 13, 1981Jul 3, 1984Gilmore Samuel ESubsea fluid conduit connections for remote controlled valvesUS4478287Jan 27, 1983Oct 23, 1984Hydril CompanyWell control method and apparatusUS4480703Nov 16, 1981Nov 6, 1984Smith International, Inc.Drilling headUS4484753Jan 31, 1983Nov 27, 1984Nl Industries, Inc.Rotary shaft sealUS4486025Mar 5, 1984Dec 4, 1984Washington Rotating Control Heads, Inc.Stripper packerUS4497592Dec 1, 1981Feb 5, 1985Armco Inc.Self-levelling underwater structureUS4500094May 24, 1982Feb 19, 1985Biffle Morris SHigh pressure rotary stripperUS4502534Dec 13, 1982Mar 5, 1985Hydril CompanyFlow diverterUS4509405Jan 11, 1982Apr 9, 1985Nl Industries, Inc.Control valve system for blowout preventersUS4524832Nov 30, 1983Jun 25, 1985Hydril CompanyDiverter/BOP system and method for a bottom supported offshore drilling rigUS4526243Nov 23, 1981Jul 2, 1985Smith International, Inc.Drilling headUS4527632Jun 7, 1983Jul 9, 1985Geard ChaudotSystem for increasing the recovery of product fluids from underwater marine depositsUS4529210Apr 1, 1983Jul 16, 1985Biffle Morris SDrilling media injection for rotating blowout preventorsUS4531580Jul 7, 1983Jul 30, 1985Cameron Iron Works, Inc.Rotating blowout preventersUS4531591 *Aug 24, 1983Jul 30, 1985Washington Rotating Control HeadsDrilling head method and apparatusUS4531593Mar 11, 1983Jul 30, 1985Elliott Guy R BSubstantially self-powered fluid turbinesUS4531951Dec 19, 1983Jul 30, 1985Cellu Products CompanyMethod and apparatus for recovering blowing agent in foam productionUS4533003Mar 8, 1984Aug 6, 1985A-Z International CompanyDrilling apparatus and cutter thereforUS4540053Dec 6, 1983Sep 10, 1985Smith International, Inc.Breech block hanger support well completion methodUS4546828Jan 10, 1984Oct 15, 1985Hydril CompanyDiverter system and blowout preventerUS4553591Apr 12, 1984Nov 19, 1985Mitchell Richard TOil well drilling apparatusUS4566494Mar 1, 1985Jan 28, 1986Hydril CompanyVent line systemUS4575426Jun 19, 1984Mar 11, 1986Exxon Production Research Co.Method and apparatus employing oleophilic brushes for oil spill clean-upUS4595343Sep 12, 1984Jun 17, 1986Baker Drilling Equipment CompanyRemote mud pump control apparatusUS4597447May 11, 1984Jul 1, 1986Hydril CompanyDiverter/bop system and method for a bottom supported offshore drilling rigUS4597448Nov 30, 1983Jul 1, 1986Smith International, Inc.Subsea wellhead systemUS4610319Oct 15, 1984Sep 9, 1986Kalsi Manmohan SHydrodynamic lubricant seal for drill bitsUS4611661Apr 15, 1985Sep 16, 1986Vetco Offshore Industries, Inc.Retrievable exploration guide base/completion guide base systemUS4615544Feb 16, 1982Oct 7, 1986Smith International, Inc.Subsea wellhead systemUS4618314Nov 9, 1984Oct 21, 1986Hailey Charles DFluid injection apparatus and method used between a blowout preventer and a choke manifoldUS4621655Mar 4, 1985Nov 11, 1986Hydril CompanyMarine riser fill-up valveUS4623020Sep 25, 1984Nov 18, 1986Cactus Wellhead Equipment Co., Inc.Communication joint for use in a wellUS4626135Oct 22, 1984Dec 2, 1986Hydril CompanyMarine riser well control method and apparatusUS4630680Mar 15, 1985Dec 23, 1986Hydril CompanyWell control method and apparatusUS4632188Sep 4, 1985Dec 30, 1986Atlantic Richfield CompanySubsea wellhead apparatusUS4646826Jul 29, 1985Mar 3, 1987A-Z International Tool CompanyWell string cutting apparatusUS4646844Dec 24, 1984Mar 3, 1987Hydril CompanyDiverter/bop system and method for a bottom supported offshore drilling rigUS4651830Jul 3, 1985Mar 24, 1987Cameron Iron Works, Inc.Marine wellhead structureUS4660863Jul 24, 1985Apr 28, 1987A-Z International Tool CompanyCasing patch sealUS4688633Mar 26, 1986Aug 25, 1987Barkley Stephen HWellhead connecting apparatusUS4690220May 1, 1985Sep 1, 1987Texas Iron Works, Inc.Tubular member anchoring arrangement and methodUS4697484Sep 13, 1985Oct 6, 1987Gerhard KleeRotating drilling headUS4709900Mar 20, 1986Dec 1, 1987Einar DyhrChoke valve especially used in oil and gas wellsUS4712620Jan 31, 1985Dec 15, 1987Vetco Gray Inc.Upper marine riser packageUS4719937Nov 29, 1985Jan 19, 1988Hydril CompanyMarine riser anti-collapse valveUS4722615Apr 14, 1986Feb 2, 1988A-Z International Tool CompanyDrilling apparatus and cutter thereforUS4727942Nov 5, 1986Mar 1, 1988Hughes Tool CompanyCompensator for earth boring bitsUS4736799Jan 14, 1987Apr 12, 1988Cameron Iron Works Usa, Inc.Subsea tubing hangerUS4745970Mar 17, 1986May 24, 1988Arkoma Machine ShopRotating headUS4749035Apr 30, 1987Jun 7, 1988Cameron Iron Works Usa, Inc.Tubing packerUS4754820Jun 18, 1986Jul 5, 1988Drilex Systems, Inc.Drilling head with bayonet couplingUS4757584Apr 29, 1987Jul 19, 1988Kleinewefers GmbhRoll for use in calenders and the likeUS4759413Apr 13, 1987Jul 26, 1988Drilex Systems, Inc.Method and apparatus for setting an underwater drilling systemUS4765404Apr 13, 1987Aug 23, 1988Drilex Systems, Inc.Whipstock packer assemblyUS4783084Jul 21, 1986Nov 8, 1988Biffle Morris SHead for a rotating blowout preventorUS4807705Sep 11, 1987Feb 28, 1989Cameron Iron Works Usa, Inc.Casing hanger with landing shoulder seal insertUS4813495May 5, 1987Mar 21, 1989Conoco Inc.Method and apparatus for deepwater drillingUS4817724Aug 19, 1988Apr 4, 1989Vetco Gray Inc.Diverter system test tool and methodUS4822212Oct 28, 1987Apr 18, 1989Amoco CorporationSubsea template and method for using the sameUS4825938Aug 3, 1987May 2, 1989Kenneth DavisRotating blowout preventor for drilling rigUS4828024Nov 9, 1988May 9, 1989Hydril CompanyDiverter system and blowout preventerUS4832126Jul 24, 1986May 23, 1989Hydril CompanyDiverter system and blowout preventerUS4836289Feb 11, 1988Jun 6, 1989Southland Rentals, Inc.Method and apparatus for performing wireline operations in a wellUS4865137Apr 22, 1988Sep 12, 1989Drilex Systems, Inc.Drilling apparatus and cutterUS4882830Feb 3, 1989Nov 28, 1989Carstensen Kenneth JMethod for improving the integrity of coupling sections in high performance tubing and casingUS4909327Jan 25, 1989Mar 20, 1990Hydril CompanyMarine riserUS4949796Mar 7, 1989Aug 21, 1990Williams John RDrilling head seal assemblyUS4955436Dec 18, 1989Sep 11, 1990Johnston Vaughn RSeal apparatusUS4955949Feb 1, 1989Sep 11, 1990Drilex Systems, Inc.Mud saver valve with increased flow check valveUS4962819Feb 1, 1989Oct 16, 1990Drilex Systems, Inc.Mud saver valve with replaceable inner sleeveUS4971148Jan 30, 1989Nov 20, 1990Hydril CompanyFlow diverterUS4984636Feb 21, 1989Jan 15, 1991Drilex Systems, Inc.Geothermal wellhead repair unitUS4995464Aug 25, 1989Feb 26, 1991Dril-Quip, Inc.Well apparatus and methodUS5009265Sep 7, 1989Apr 23, 1991Drilex Systems, Inc.Packer for wellhead repair unitUS5022472Nov 14, 1989Jun 11, 1991Masx Energy Services Group, Inc.Hydraulic clamp for rotary drilling headUS5028056Nov 24, 1986Jul 2, 1991The Gates Rubber CompanyFiber composite sealing elementUS5035292Jan 11, 1989Jul 30, 1991Masx Energy Service Group, Inc.Whipstock starter mill with pressure drop tattletaleUS5040600Jun 20, 1990Aug 20, 1991Drilex Systems, Inc.Geothermal wellhead repair unitUS5048621Aug 10, 1990Sep 17, 1991Masx Energy Services Group, Inc.Adjustable bent housing for controlled directional drillingUS5062450Oct 5, 1990Nov 5, 1991Masx Energy Services Group, Inc.Valve body for oilfield applicationsUS5062479Jul 31, 1990Nov 5, 1991Masx Energy Services Group, Inc.Stripper rubbers for drilling headsUS5072795Jan 22, 1991Dec 17, 1991Camco International Inc.Pressure compensator for drill bit lubrication systemUS5076364Mar 19, 1991Dec 31, 1991Shell Oil CompanyGas hydrate inhibitionUS5082020Dec 5, 1990Jan 21, 1992Masx Energy Services Group, Inc.Valve body for oilfield applicationsUS5085277Nov 5, 1990Feb 4, 1992The British Petroleum Company, P.L.C.Sub-sea well injection systemUS5101897Jan 14, 1991Apr 7, 1992Camco International Inc.Slip mechanism for a well toolUS5137084Dec 20, 1990Aug 11, 1992The Sydco System, Inc.Rotating headUS5147559May 1, 1991Sep 15, 1992Brophey Robert WControlling cone of depression in a well by microprocessor control of modulating valveUS5154231Sep 19, 1990Oct 13, 1992Masx Energy Services Group, Inc.Whipstock assembly with hydraulically set anchorUS5163514Aug 12, 1991Nov 17, 1992Abb Vetco Gray Inc.Blowout preventer isolation test toolUS5165480Aug 1, 1991Nov 24, 1992Camco International Inc.Method and apparatus of locking closed a subsurface safety systemUS5178215Jul 22, 1991Jan 12, 1993Folsom Metal Products, Inc.Rotary blowout preventer adaptable for use with both kelly and overhead drive mechanismsUS5182979Mar 2, 1992Feb 2, 1993Caterpillar Inc.Linear position sensor with equalizing meansUS5184686May 3, 1991Feb 9, 1993Shell Offshore Inc.Method for offshore drilling utilizing a two-riser systemUS5195754May 20, 1991Mar 23, 1993Kalsi Engineering, Inc.Laterally translating seal carrier for a drilling mud motor sealed bearing assemblyUS5213158Dec 20, 1991May 25, 1993Masx Entergy Services Group, Inc.Dual rotating stripper rubber drilling headUS5215151Sep 26, 1991Jun 1, 1993Cudd Pressure Control, Inc.Method and apparatus for drilling bore holes under pressureUS5224557Jan 11, 1993Jul 6, 1993Folsom Metal Products, Inc.Rotary blowout preventer adaptable for use with both kelly and overhead drive mechanismsUS5230520Mar 13, 1992Jul 27, 1993Kalsi Engineering, Inc.Hydrodynamically lubricated rotary shaft seal having twist resistant geometryUS5243187Jun 28, 1990Sep 7, 1993Teldix GmbhHigh resolution absolute encoder for position measurementUS5251869Dec 30, 1992Oct 12, 1993Mason Benny MRotary blowout preventerUS5255745Jun 18, 1992Oct 26, 1993Cooper Industries, Inc.Remotely operable horizontal connection apparatus and methodUS5277249Jan 11, 1993Jan 11, 1994Folsom Metal Products, Inc.Rotary blowout preventer adaptable for use with both kelly and overhead drive mechanismsUS5279365Jan 11, 1993Jan 18, 1994Folsom Metal Products, Inc.Rotary blowout preventer adaptable for use with both kelly and overhead drive mechanismsUS5305839Jan 19, 1993Apr 26, 1994Masx Energy Services Group, Inc.Turbine pump ring for drilling headsUS5320325Aug 2, 1993Jun 14, 1994Hydril CompanyPosition instrumented blowout preventerUS5322137Oct 22, 1992Jun 21, 1994The Sydco SystemRotating head with elastomeric member rotating assemblyUS5325925Jun 26, 1992Jul 5, 1994Ingram Cactus CompanySealing method and apparatus for wellheadsUS5348107Feb 26, 1993Sep 20, 1994Smith International, Inc.Pressure balanced inner chamber of a drilling headUS5375476Sep 30, 1993Dec 27, 1994Wetherford U.S., Inc.Stuck pipe locator systemUS5427179Dec 16, 1993Jun 27, 1995Smith International, Inc.Retrievable whipstockUS5431220Mar 24, 1994Jul 11, 1995Smith International, Inc.Whipstock starter mill assemblyUS5443129Jul 22, 1994Aug 22, 1995Smith International, Inc.Apparatus and method for orienting and setting a hydraulically-actuatable tool in a boreholeUS5495872Jan 31, 1994Mar 5, 1996Integrity Measurement PartnersFlow conditioner for more accurate measurement of fluid flowUS5529093Mar 24, 1995Jun 25, 1996Integrity Measurement PartnersFlow conditioner profile plate for more accurate measurement of fluid flowUS5588491Aug 10, 1995Dec 31, 1996Varco Shaffer, Inc.Rotating blowout preventer and methodUS5607019Sep 11, 1995Mar 4, 1997Abb Vetco Gray Inc.Adjustable mandrel hanger for a jackup drilling rigUS5647444Aug 23, 1996Jul 15, 1997Williams; John R.Rotating blowout preventorUS5657820Dec 14, 1995Aug 19, 1997Smith International, Inc.Two trip window cutting systemUS5662171Oct 4, 1996Sep 2, 1997Varco Shaffer, Inc.Rotating blowout preventer and methodUS5662181Oct 22, 1996Sep 2, 1997Williams; John R.Rotating blowout preventerUS5671812Apr 4, 1996Sep 30, 1997Abb Vetco Gray Inc.Hydraulic pressure assisted casing tensioning systemUS5678829Jun 7, 1996Oct 21, 1997Kalsi Engineering, Inc.Hydrodynamically lubricated rotary shaft seal with environmental side grooveUS5735502Dec 18, 1996Apr 7, 1998Varco Shaffer, Inc.BOP with partially equalized ram shaftsUS5738358Jan 2, 1996Apr 14, 1998Kalsi Engineering, Inc.Extrusion resistant hydrodynamically lubricated multiple modulus rotary shaft sealUS5755372Jul 20, 1995May 26, 1998Ocean Engineering & Manufacturing, Inc.Self monitoring oil pump sealUS5823541Mar 12, 1996Oct 20, 1998Kalsi Engineering, Inc.Rod seal cartridge for progressing cavity artificial lift pumpsUS5829531Jan 31, 1996Nov 3, 1998Smith International, Inc.Mechanical set anchor with slips pocketUS5848643Dec 19, 1996Dec 15, 1998Hydril CompanyRotating blowout preventerUS5873576Sep 11, 1997Feb 23, 1999Kalsi Engineering, Inc.Skew and twist resistant hydrodynamic rotary shaft sealUS5878818May 28, 1998Mar 9, 1999Smith International, Inc.Mechanical set anchor with slips pocketUS5901964Feb 6, 1997May 11, 1999John R. WilliamsSeal for a longitudinally movable drillstring componentUS5944111Nov 21, 1997Aug 31, 1999Abb Vetco Gray Inc.Internal riser tensioning systemUS6007105Feb 4, 1998Dec 28, 1999Kalsi Engineering, Inc.Swivel seal assemblyUS6016880Oct 2, 1997Jan 25, 2000Abb Vetco Gray Inc.Rotating drilling head with spaced apart sealsUS6017168Dec 22, 1997Jan 25, 2000Abb Vetco Gray Inc.Fluid assist bearing for telescopic joint of a RISER systemUS6036192Feb 16, 1999Mar 14, 2000Kalsi Engineering, Inc.Skew and twist resistant hydrodynamic rotary shaft sealUS6076606Sep 10, 1998Jun 20, 2000Weatherford/Lamb, Inc.Through-tubing retrievable whipstock systemUS6102123Feb 10, 1998Aug 15, 2000Smith International, Inc.One trip milling systemUS6102673Mar 25, 1999Aug 15, 2000Hydril CompanySubsea mud pump with reduced pulsationUS6109348Aug 20, 1997Aug 29, 2000Caraway; Miles F.Rotating blowout preventerUS6109618May 6, 1998Aug 29, 2000Kalsi Engineering, Inc.Rotary seal with enhanced lubrication and contaminant flushingUS6112810Oct 31, 1998Sep 5, 2000Weatherford/Lamb, Inc.Remotely controlled assembly for wellbore flow diverterUS6120036Jan 27, 1998Sep 19, 2000Kalsi Engineering, Inc.Extrusion resistant hydrodynamically lubricated rotary shaft sealUS6129152Oct 23, 1998Oct 10, 2000Alpine Oil Services Inc.Rotating bop and methodUS6138774Mar 2, 1998Oct 31, 2000Weatherford Holding U.S., Inc.Method and apparatus for drilling a borehole into a subsea abnormal pore pressure environmentUS6170576Feb 25, 1999Jan 9, 2001Weatherford/Lamb, Inc.Mills for wellbore operationsUS6202745Oct 7, 1998Mar 20, 2001Dril-Quip, IncWellhead apparatusUS6209663Apr 14, 1999Apr 3, 2001David G. HosieUnderbalanced drill string deployment valve method and apparatusUS6213228Jul 28, 1998Apr 10, 2001Dresser Industries Inc.Roller cone drill bit with improved pressure compensationUS6227547May 26, 1999May 8, 2001Kalsi Engineering, Inc.High pressure rotary shaft sealing mechanismUS6230824Mar 25, 1999May 15, 2001Hydril CompanyRotating subsea diverterUS6244359Apr 5, 1999Jun 12, 2001Abb Vetco Gray, Inc.Subsea diverter and rotating drilling headUS6263982Mar 2, 1999Jul 24, 2001Weatherford Holding U.S., Inc.Method and system for return of drilling fluid from a sealed marine riser to a floating drilling rig while drillingUS6273193Dec 16, 1998Aug 14, 2001Transocean Sedco Forex, Inc.Dynamically positioned, concentric riser, drilling method and apparatusUS6315302Apr 26, 2000Nov 13, 2001Kalsi Engineering, Inc.Skew resisting hydrodynamic sealUS6315813Nov 18, 1999Nov 13, 2001Northland Energy CorporationMethod of treating pressurized drilling fluid returns from a wellUS6325159Mar 25, 1999Dec 4, 2001Hydril CompanyOffshore drilling systemUS6334619May 19, 1999Jan 1, 2002Kalsi Engineering, Inc.Hydrodynamic packing assemblyUS6352129Jun 22, 2000Mar 5, 2002Shell Oil CompanyDrilling systemUS6354385Jan 10, 2000Mar 12, 2002Smith International, Inc.Rotary drilling head assemblyUS6375895Jun 14, 2000Apr 23, 2002Att Technology, Ltd.Hardfacing alloy, methods, and productsUS6382634Apr 26, 2000May 7, 2002Kalsi Engineering, Inc.Hydrodynamic seal with improved extrusion abrasion and twist resistanceUS6386291Oct 12, 2000May 14, 2002David E. ShortSubsea wellhead system and method for drilling shallow water flow formationsUS6413297Jul 27, 2000Jul 2, 2002Northland Energy CorporationMethod and apparatus for treating pressurized drilling fluid returns from a wellUS6450262Dec 8, 2000Sep 17, 2002Stewart & Stevenson Services, Inc.Riser isolation toolUS6454007Jun 30, 2000Sep 24, 2002Weatherford/Lamb, Inc.Method and apparatus for casing exit system using coiled tubingUS6457529Feb 16, 2001Oct 1, 2002Abb Vetco Gray Inc.Apparatus and method for returning drilling fluid from a subsea wellboreUS6470975Mar 1, 2000Oct 29, 2002Weatherford/Lamb, Inc.Internal riser rotating control headUS6478303Nov 3, 2000Nov 12, 2002Hoerbiger Ventilwerke GmbhSealing ring packingUS6494462Apr 26, 2000Dec 17, 2002Kalsi Engineering, Inc.Rotary seal with improved dynamic interfaceUS6504982Jun 30, 1999Jan 7, 2003AlcatelIncorporation of UV transparent perlescent pigments to UV curable optical fiber materialsUS6505691Aug 6, 2001Jan 14, 2003Hydril CompanySubsea mud pump and control systemUS6520253May 3, 2001Feb 18, 2003Abb Vetco Gray Inc.Rotating drilling head system with static sealsUS6536520Apr 17, 2000Mar 25, 2003Weatherford/Lamb, Inc.Top drive casing systemUS6536525Sep 11, 2000Mar 25, 2003Weatherford/Lamb, Inc.Methods and apparatus for forming a lateral wellboreUS6547002Apr 17, 2000Apr 15, 2003Weatherford/Lamb, Inc.High pressure rotating drilling head assembly with hydraulically removable packerUS6554016Dec 12, 2000Apr 29, 2003Northland Energy CorporationRotating blowout preventer with independent cooling circuits and thrust bearingUS6561520Feb 2, 2001May 13, 2003Kalsi Engineering, Inc.Hydrodynamic rotary coupling sealUS6581681Jun 21, 2000Jun 24, 2003Weatherford/Lamb, Inc.Bridge plug for use in a wellboreUS6607042May 17, 2001Aug 19, 2003Precision Drilling Technology Services Group Inc.Method of dynamically controlling bottom hole circulation pressure in a wellboreUS6655460Oct 12, 2001Dec 2, 2003Weatherford/Lamb, Inc.Methods and apparatus to control downhole toolsUS6685194Apr 12, 2001Feb 3, 2004Lannie DietleHydrodynamic rotary seal with varying slopeUS6702012Feb 14, 2003Mar 9, 2004Weatherford/Lamb, Inc.High pressure rotating drilling head assembly with hydraulically removable packerUS6708762Jan 27, 2003Mar 23, 2004Weatherford/Lamb, Inc.Methods and apparatus for forming a lateral wellboreUS6720764Apr 16, 2002Apr 13, 2004Thomas Energy Services Inc.Magnetic sensor system useful for detecting tool joints in a downhold tubing stringUS6725951Sep 27, 2001Apr 27, 2004Diamond Rotating Heads, Inc.Erosion resistent drilling head assemblyUS6732804May 23, 2002May 11, 2004Weatherford/Lamb, Inc.Dynamic mudcap drilling and well control systemUS6749172Apr 25, 2003Jun 15, 2004Precision Drilling Technology Services Group, Inc.Rotating blowout preventer with independent cooling circuits and thrust bearingUS6767016Apr 12, 2001Jul 27, 2004Jeffrey D. GobeliHydrodynamic rotary seal with opposed tapering seal lipsUS6843313Jun 11, 2001Jan 18, 2005Oil Lift Technology, Inc.Pump drive head with stuffing boxUS6851476Aug 2, 2002Feb 8, 2005Weather/Lamb, Inc.Dual sensor freepoint toolUS6877565Dec 26, 2002Apr 12, 2005Agr Services AsArrangement for the removal of cuttings and gas arising from drilling operationsUS6886631Aug 5, 2002May 3, 2005Weatherford/Lamb, Inc.Inflation tool with real-time temperature and pressure probesUS6896048Dec 20, 2002May 24, 2005Varco I/P, Inc.Rotary support tableUS6896076Dec 3, 2002May 24, 2005Abb Vetco Gray Inc.Rotating drilling head gripperUS6904981Feb 18, 2003Jun 14, 2005Shell Oil CompanyDynamic annular pressure control apparatus and methodUS6913092Jul 23, 2001Jul 5, 2005Weatherford/Lamb, Inc.Method and system for return of drilling fluid from a sealed marine riser to a floating drilling rig while drillingUS6945330Aug 5, 2002Sep 20, 2005Weatherford/Lamb, Inc.Slickline power control interfaceUS7004444Jun 15, 2004Feb 28, 2006Precision Drilling Technology Services Group, Inc.Rotating blowout preventer with independent cooling circuits and thrust bearingUS7007913Jun 15, 2004Mar 7, 2006Precision Drilling Technology Services Group, Inc.Rotating blowout preventer with independent cooling circuits and thrust bearingUS7011167May 15, 2001Mar 14, 2006VOEST-ALPINE Bergetechnik Gesellschaft m.b.H.Device for sealing a drill hole and for discharging drillings or stripped extraction materialUS7025130Dec 1, 2003Apr 11, 2006Weatherford/Lamb, Inc.Methods and apparatus to control downhole toolsUS7028777Oct 16, 2003Apr 18, 2006Dril-Quip, Inc.Open water running tool and lockdown sleeve assemblyUS7032691Oct 30, 2003Apr 25, 2006Stena Drilling Ltd.Underbalanced well drilling and productionUS7040394Oct 31, 2002May 9, 2006Weatherford/Lamb, Inc.Active/passive seal rotating control headUS7044237Oct 2, 2002May 16, 2006Impact Solutions Group LimitedDrilling system and methodUS7073580Sep 10, 2004Jul 11, 2006Weatherford/Lamb, Inc.Inflation tool with real-time temperature and pressure probesUS7077212Sep 20, 2002Jul 18, 2006Weatherford/Lamb, Inc.Method of hydraulically actuating and mechanically activating a downhole mechanical apparatusUS7080685Feb 20, 2004Jul 25, 2006Weatherford/Lamb, Inc.High pressure rotating drilling head assembly with hydraulically removable packerUS7086481Oct 11, 2002Aug 8, 2006Weatherford/LambWellbore isolation apparatus, and method for tripping pipe during underbalanced drillingUS7152680Aug 23, 2005Dec 26, 2006Weatherford/Lamb, Inc.Slickline power control interfaceUS7159669Oct 28, 2002Jan 9, 2007Weatherford/Lamb, Inc.Internal riser rotating control headUS7165610Sep 8, 2004Jan 23, 2007Cameron International CorporationRemovable sealUS7174956Feb 11, 2004Feb 13, 2007Williams John RStripper rubber adapterUS7178600Feb 20, 2004Feb 20, 2007Weatherford/Lamb, Inc.Apparatus and methods for utilizing a downhole deployment valveUS7191840Mar 5, 2004Mar 20, 2007Weatherford/Lamb, Inc.Casing running and drilling systemUS7198098Apr 22, 2004Apr 3, 2007Williams John RMechanical connection systemUS7204315Oct 17, 2001Apr 17, 2007Weatherford/Lamb, Inc.Dual valve well control in underbalanced wellsUS7219729Oct 1, 2003May 22, 2007Weatherford/Lamb, Inc.Permanent downhole deployment of optical sensorsUS7237618Feb 20, 2004Jul 3, 2007Williams John RStripper rubber insert assemblyUS7237623Sep 19, 2003Jul 3, 2007Weatherford/Lamb, Inc.Method for pressurized mud cap and reverse circulation drilling from a floating drilling rig using a sealed marine riserUS7240727May 12, 2004Jul 10, 2007Williams John RArmored stripper rubberUS7243958Apr 22, 2004Jul 17, 2007Williams John RSpring-biased pin connection systemUS7255173Oct 1, 2003Aug 14, 2007Weatherford/Lamb, Inc.Instrumentation for a downhole deployment valveUS7258171Nov 21, 2005Aug 21, 2007Weatherford/Lamb, Inc.Internal riser rotating control headUS7278494Nov 28, 2006Oct 9, 2007Williams John RStripper rubber insert assemblyUS7278496Nov 2, 2005Oct 9, 2007Christian LeuchtenbergDrilling system and methodUS7296628Nov 18, 2005Nov 20, 2007Mako Rentals, Inc.Downhole swivel apparatus and methodUS7308954Jun 2, 2003Dec 18, 2007Stacey Oil Services, Ltd.Rotating diverter headUS7325610Mar 5, 2004Feb 5, 2008Weatherford/Lamb, Inc.Methods and apparatus for handling and drilling with tubulars or casingUS7334633Dec 14, 2006Feb 26, 2008Williams John RStripper rubber adapterUS7347261Sep 8, 2005Mar 25, 2008Schlumberger Technology CorporationMagnetic locator systems and methods of use at a well siteUS7350590Nov 5, 2002Apr 1, 2008Weatherford/Lamb, Inc.Instrumentation for a downhole deployment valveUS7363860Nov 30, 2005Apr 29, 2008Weatherford/Lamb, Inc.Non-explosive two component initiatorUS7367411Nov 2, 2005May 6, 2008Secure Drilling International, L.P.Drilling system and methodUS7380590Aug 19, 2004Jun 3, 2008Sunstone CorporationRotating pressure control headUS7380591Feb 15, 2007Jun 3, 2008Williams John RMechanical connection systemUS7380610Aug 29, 2007Jun 3, 2008Williams John RStripper rubber insert assemblyUS7383876Feb 8, 2005Jun 10, 2008Weatherford/Lamb, Inc.Cutting tool for use in a wellbore tubularUS7389183Oct 18, 2004Jun 17, 2008Weatherford/Lamb, Inc.Method for determining a stuck point for pipe, and free point logging toolUS7392860Mar 7, 2006Jul 1, 2008Johnston Vaughn RStripper rubber on a steel core with an integral sealing gasketUS7413018Jul 9, 2004Aug 19, 2008Weatherford/Lamb, Inc.Apparatus for wellbore communicationUS7416021Jun 4, 2007Aug 26, 2008Williams John RArmored stripper rubberUS7416226Jun 4, 2007Aug 26, 2008Williams John RSpring-biased pin connection systemUS7448454Mar 23, 2004Nov 11, 2008Weatherford/Lamb, Inc.Method and system for return of drilling fluid from a sealed marine riser to a floating drilling rig while drillingUS7451809Jun 21, 2005Nov 18, 2008Weatherford/Lamb, Inc.Apparatus and methods for utilizing a downhole deployment valveUS7475732May 3, 2007Jan 13, 2009Weatherford/Lamb, Inc.Instrumentation for a downhole deployment valveUS7487837 *Nov 23, 2004Feb 10, 2009Weatherford/Lamb, Inc.Riser rotating control deviceUS7513300Mar 20, 2007Apr 7, 2009Weatherford/Lamb, Inc.Casing running and drilling systemUS7559359Jul 14, 2009Williams John RSpring preloaded bearing assembly and well drilling equipment comprising sameUS7635034Dec 22, 2009Theresa J. Williams, legal representativeSpring load seal assembly and well drilling equipment comprising sameUS7650950Sep 10, 2007Jan 26, 2010Secure Drilling International, L.P.Drilling system and methodUS7654325Feb 2, 2010Weatherford/Lamb, Inc.Methods and apparatus for handling and drilling with tubulars or casingUS7669649Mar 2, 2010Theresa J. Williams, legal representativeStripper rubber with integral retracting retention member connection apparatusUS7699109Nov 6, 2006Apr 20, 2010Smith InternationalRotating control device apparatus and methodUS7708089Apr 15, 2008May 4, 2010Theresa J. Williams, legal representativeBreech lock stripper rubber pot mounting structure and well drilling equipment comprising sameUS7712523Mar 14, 2003May 11, 2010Weatherford/Lamb, Inc.Top drive casing systemUS7717169Feb 7, 2008May 18, 2010Theresa J. Williams, legal representativeBearing assembly system with integral lubricant distribution and well drilling equipment comprising sameUS7717170Feb 7, 2008May 18, 2010Williams John RStripper rubber pot mounting structure and well drilling equipment comprising sameUS7726416Feb 7, 2008Jun 1, 2010Theresa J. Williams, legal representativeBearing assembly retaining apparatus and well drilling equipment comprising sameUS7743823Jun 29, 2010Sunstone Technologies, LlcForce balanced rotating pressure control deviceUS7762320Jul 27, 2010Williams John RHeat exchanger system and method of use thereof and well drilling equipment comprising sameUS7766100Aug 3, 2010Theresa J. Williams, legal representativeTapered surface bearing assembly and well drilling equiment comprising sameUS7779903May 6, 2005Aug 24, 2010Weatherford/Lamb, Inc.Solid rubber packer for a rotating control deviceUS7789132Sep 7, 2010Theresa J. Williams, legal representativeStripper rubber retracting connection systemUS7789172Sep 7, 2010Williams John RTapered bearing assembly cover plate and well drilling equipment comprising sameUS7793719Sep 14, 2010Weatherford/Lamb, Inc.Top drive casing systemUS7798250Sep 21, 2010Theresa J. Williams, legal representativeBearing assembly inner barrel and well drilling equipment comprising sameUS7802635Dec 12, 2007Sep 28, 2010Smith International, Inc.Dual stripper rubber cartridge with leak detectionUS7823665Aug 7, 2007Nov 2, 2010Weatherford/Lamb, Inc.Milling of cemented tubularsUS7836946Mar 2, 2006Nov 23, 2010Weatherford/Lamb, Inc.Rotating control head radial seal protection and leak detection systemsUS7836976Apr 5, 2007Nov 23, 2010Allied Construction Products, L.L.C.Underground piercing toolUS20030106712Oct 28, 2002Jun 12, 2003Weatherford/Lamb, Inc.Internal riser rotating control headUS20030164276Jan 23, 2003Sep 4, 2003Weatherford/Lamb, Inc.Top drive casing systemUS20040017190Jul 17, 2003Jan 29, 2004Mcdearmon Graham F.Apparatus and method for absolute angular position sensingUS20050151107Dec 27, 2004Jul 14, 2005Jianchao ShuFluid control system and stem jointUS20060037782Aug 1, 2005Feb 23, 2006Martin-Marshall Peter SDiverter headsUS20060108119Nov 23, 2004May 25, 2006Weatherford/Lamb, Inc.Riser rotating control deviceUS20060144622Mar 2, 2006Jul 6, 2006Weatherford/Lamb, Inc.Rotating control head radial seal protection and leak detection systemsUS20060157282Oct 20, 2005Jul 20, 2006Tilton Frederick TManaged pressure drillingUS20060191716Apr 13, 2006Aug 31, 2006Gavin HumphreysWell drilling and production using a surface blowout preventerUS20070051512Sep 8, 2005Mar 8, 2007Schlumberger Technology CorporationMagnetic Locator Systems and Methods of Use at a Well SiteUS20070095540Oct 20, 2006May 3, 2007John KoziczApparatus and method for managed pressure drillingUS20070163784Jul 25, 2006Jul 19, 2007Bailey Thomas FHigh pressure rotating drilling head assembly with hydraulically removable packerUS20080169107Jan 15, 2008Jul 17, 2008Redlinger Thomas MApparatus and method for stabilization of downhole toolsUS20080210471Mar 31, 2008Sep 4, 2008Weatherford/Lamb, Inc.Rotating control device docking stationUS20080236819Feb 12, 2008Oct 2, 2008Weatherford/Lamb, Inc.Position sensor for determining operational condition of downhole toolUS20080245531Apr 4, 2008Oct 9, 2008Joe NoskeDownhole deployment valvesUS20090025930Jul 25, 2008Jan 29, 2009David IblingsContinuous flow drilling systems and methodsUS20090101351Oct 19, 2007Apr 23, 2009Weatherford/Lamb, Inc.Universal marine diverter converterUS20090101411Oct 23, 2007Apr 23, 2009Weatherford/Lamb, Inc.Low profile rotating control deviceUS20090139724Feb 6, 2009Jun 4, 2009Weatherford/Lamb, Inc.Latch position indicator system and methodUS20090152006Dec 12, 2007Jun 18, 2009Smith International, Inc.Dual stripper rubber cartridge with leak detectionUS20090166046Jul 12, 2006Jul 2, 2009Per Espen EdvardsonSystem and Method for Dynamic Sealing Of a Drill StringUS20090200747Apr 15, 2008Aug 13, 2009Williams John RBreech lock stripper rubber pot mounting structure and well drilling equipment comprising sameUS20090211239Jul 12, 2006Aug 27, 2009Siem Wis AsPressure accumulator to establish sufficient power to handle and operate external equipment and use thereofUS20090236144Feb 9, 2007Sep 24, 2009Todd Richard JManaged pressure and/or temperature drilling system and methodUS20090301723Jun 4, 2008Dec 10, 2009Gray Kevin LInterface for deploying wireline tools with non-electric stringUS20100008190Jan 14, 2010Gray Kevin LApparatus and Method for Data Transmission from a Rotating Control DeviceUSRE38249Dec 22, 1998Sep 16, 2003James D. BrugmanRotating blowout preventer and methodAU199927822B2 Title not availableAU200028183A1 Title not availableAU200028183B2 Title not availableCA2363132A1Mar 1, 2000Sep 8, 2000Weatherford LambInternal riser rotating control headCA2447196A1Oct 28, 2003Apr 30, 2004Weatherford LambActive/passive seal rotating control headEP267140B1 Title not availableEP0290250A2May 5, 1988Nov 9, 1988Conoco Inc.Method and apparatus for deepwater drillingEP0290250A3May 5, 1988Nov 8, 1989Conoco Inc.Method and apparatus for deepwater drillingEP1375817A1Jun 24, 2002Jan 2, 2004Services Petroliers SchlumbergerUnderbalance drilling downhole chokeEP1519003A1Sep 24, 2003Mar 30, 2005Cooper Cameron CorporationRemovable sealEP1659260A2Nov 23, 2005May 24, 2006Weatherford/Lamb, Inc.Riser rotating control deviceGB2019921A Title not availableGB2067235A Title not availableGB2394741A Title not availableGB2449010A Title not availableWO1999045228A1Feb 24, 1999Sep 10, 1999Weatherford/Lamb, Inc.Method and apparatus for drilling a borehole into a subsea abnormal pore pressure environmentWO1999050524A2Mar 26, 1999Oct 7, 1999Hydril CompanySubsea mud pumpWO1999050524A3Mar 26, 1999Dec 2, 1999Hydril CoSubsea mud pumpWO1999051852A1Apr 6, 1999Oct 14, 1999Abb Vetco Gray Inc.Subsea diverter and rotating drilling headWO2000052299A1Mar 1, 2000Sep 8, 2000Weatherford/Lamb, Inc.Internal riser rotating control headWO2000052300A1Mar 1, 2000Sep 8, 2000Weatherford/Lamb, Inc.Rotating blowout preventerWO2002050398A1Dec 14, 2001Jun 27, 2002Impact Engineering Solutions LimitedCloded loop fluid-handing system for well drillingWO2003071091A1Feb 19, 2003Aug 28, 2003Shell Internationale Research Maatschappij B.V.Dynamic annular pressure control apparatus and methodWO2006088379A1Feb 17, 2006Aug 24, 2006Agr Subsea AsCentralization and running tool and methodWO2007092956A2Feb 9, 2007Aug 16, 2007Weatherford/Lamb, Inc.Managed pressure and/or temperature drilling system and methodWO2008133523A1Apr 4, 2008Nov 6, 2008Siem Wis AsSeal for a drill stringWO2008156376A1Jun 20, 2008Dec 24, 2008Siem Wis AsDevice and method for maintaining constant pressure on, and flow drill fluid, in a drill stringWO2009017418A1Jul 24, 2008Feb 5, 2009Siem Wis AsSealing arrangement, and corresponding method* Cited by examinerNon-Patent CitationsReference1"2003 SPE Calendar," Society of Petroleum Engineers, Google cache of http:/www.spe.org/spe/cda/views/events/eventMaster/0,1470,1648-2194-632303.00.html; for "mud cap drilling", 2 pages (2001).2"2003 SPE Calendar," Society of Petroleum Engineers, Google cache of http:/www.spe.org/spe/cda/views/events/eventMaster/0,1470,1648—2194—632303.00.html; for "mud cap drilling", 2 pages (2001).3"BG in the Caspian region," SPE Review, Issue 164, 3 unnumbered pages (May 2003).4"Determine in the Safe Application of Underbalanced Drilling Technologies in Marine Environments -Technical Proposal," Maurer Technology, Inc., Cover Page and pp. 2-13 (Jun. 17, 2002).5"Determine in the Safe Application of Underbalanced Drilling Technologies in Marine Environments —Technical Proposal," Maurer Technology, Inc., Cover Page and pp. 2-13 (Jun. 17, 2002).6"Drilling conference promises to be informative," Drilling Contractor, p. 10 (Jan./Feb. 2002).7"Drilling equipment: Improvements from data recording to slim hole," Drilling Contractor, pp. 30-32, (Mar./Apr. 2000).8"Field Cases as of Mar. 3, 2003," Impact Fluid Solutions, 6 pages (Mar. 3, 2003).9"History and Development of a Rotating Preventer," by A. Cress, Rick Stone, and Mike Tangedahl, IADC/SPE 23931, 1992 IADC/SPE Drilling Conference, Feb. 1992, pp. 757-773.10"JIP's Worl Brightens Outlook for UBD in Deep Waters" by Edson Yoshihito Nakagawa, Helio Santos and Jose Carlos Cunha, American Oil & Gas Reporter, Apr. 1999, pp. 53, 56, 58-60 and 63.11"Oilfield Glossary: reverse-circulating valve," Schlumberger Limited, 1 page (2003).12"PETEX Publications," Petroleum Extension Service, University of Texas at Austin, 12 pages, (last modified Dec. 6, 2002).13"Pressure Control While Drilling," Shaffer� A Varco Company, Rev. A (2 unnumbered pages).14"Pressured Mud Cap Drilling from a Semi-Submersible Drilling Rig," J.H. Terwogt, SPE, L.B. Makiaho and N. van Beelen, SPE, Shell Malaysia Exploration and Production; B.J. Gedge, SPE, and J. Jenkins, Weatherford Drilling and Well Services (6 pages total); � 2005 (This paper was prepared for presentation at the SPE/IADC Drilling Conference held in Amsterdam, The Netherlands, Feb. 23-25, 2005).15"RiserCap(TM) Materials Presented at the 1999 LSU/MMS/IADC Well Control Workshop", by Williams Tool Company, Inc., Mar. 24-25, pp. 1-14.16"RiserCap™ Materials Presented at the 1999 LSU/MMS/IADC Well Control Workshop", by Williams Tool Company, Inc., Mar. 24-25, pp. 1-14.17"RPM System 3000(TM) Rotating Blowout Preventer, Setting a new standard in Well Control," by Techcorp Industries, Undated, 4 pages.18"RPM System 3000™ Rotating Blowout Preventer, Setting a new standard in Well Control," by Techcorp Industries, Undated, 4 pages.19"Seal-Tech 1500 PSI Rotating Blowout Preventer," Undated, 3 pages.20"Technical Training Courses," Parker Drilling Co., http:/www.parkerdrilling.com/news/tech.html, 5 pages (last visited, Sep. 5, 2003).21"The 1999 LSU/MMS Well Control Workshop: An overview," by John Rogers Smith. World Oil, Jun. 1999. Cover page and pp. 4, 41-42, and 44-45.22"Underbalanced and Air Drilling," GCI, Inc., http:/www.ogci.com/course-info.asp?counselD=410, 2 pages, (2003).23"Underbalanced and Air Drilling," GCI, Inc., http:/www.ogci.com/course—info.asp?counselD=410, 2 pages, (2003).24"Weatherford UnderBalanced Services: General Underbalance Presentation to the DTI," 71 unnumbered pages, � 2002.251966-1967 Composite Catalog-Grant Rotating Drilling Head for Air, Gas or Mud Drilling (1 page).261976-1977 Composite Catalog Grant Oil Tool Company Rotating Drilling Head Models 7068, 7368, 8068 (Patented), Equally Effective with Air, Gas, or Mud Circulation Media (3 pages).272003/0106712 Family Lookup Report (Jun. 15, 2006) (5 pages).286,470,975 Family Lookup Report (Jun. 15, 2006) (5 pages).29A reprint from the Oct. 9, 1995 edition of Oil & Gas Journal, "Rotating control head applications increasing," by Adam T. Bourgoyne, Jr., Copyright 1995 by PennWell Publishing Company (6 pages).30A Subsea Rotating Control Head for Riserless Drilling Applications; Daryl A. Bourgoyne, Adam T. Bourgoyne, and Don Hannegan-1998 (International Association of Drilling Contractors International Deep Water Well Control Conference held in Houston, Texas, Aug. 26-27, 1998) (14 pages).31A Subsea Rotating Control Head for Riserless Drilling Applications; Daryl A. Bourgoyne, Adam T. Bourgoyne, and Don Hannegan—1998 (International Association of Drilling Contractors International Deep Water Well Control Conference held in Houston, Texas, Aug. 26-27, 1998) (14 pages).32AC 2-Wire Tubular Sensors, Balluff product catalog pp. 1.109-1.120 (12 pages) (no. date).33American Petroleum Institute Specification for Drill Through Equipment—Rotating Control Devices, API Specification 16RCD, First Edition, Feb. 2005 (84 pages).34An article-The Brief Jan. '96, The Brief's Guest Columnists, Williams Tool Co., Inc., Communicating Dec. 13, 1995 (Fort Smith, Arkansas), The When? and Why? of Rotating Control Head Usage, Copyright � Murphy Publishing, Inc. 1996 (2 pages).35An article—The Brief Jan. '96, The Brief's Guest Columnists, Williams Tool Co., Inc., Communicating Dec. 13, 1995 (Fort Smith, Arkansas), The When? and Why? of Rotating Control Head Usage, Copyright � Murphy Publishing, Inc. 1996 (2 pages).36Analog Inductive Sensors, Balluff product catalog pp. 1.157-1.170 (14 pages) (no. date).37Antonio C.V.M. Lage, Helio, Santos and Paulo R.C. Silva, Drilling With Aerated Drilling Fluid From a Floating Unit Part 2: Drilling the Well, SPE 71361, 11 pages (�2001, Society of Petroleum Engineers, Inc.).38Apr. 1998 Offshore Drilling with Light Weight Fluids Joint Industry Project Presentation (9 unnumbered pages).39AU S/N 27822/99 Examination Report corresponding to US Patent No. 6,138,774 (1 page) (Oct. 15, 2001).40AU S/N 28181/00 Examination Report corresponding to US Patent No. 6,263,982 (1 page) (Sep. 6, 2002).41AU S/N 28183/00 Examination Report corresponding to US Patent No. 6,470,975 (1 page) (Sep. 9, 2002).42Avoiding Explosive Unloading of Gas in a Deep Water Riser When SOBM in Use; Colin P. Leach & Joseph R. Roche-1998 (The Paper Describes an Application for the Hydril Gas Handler, The Hydril GH 211-2000 Gas Handler is Depicted in Figure 1 of the Paper) (9 unnumbered pages).43Avoiding Explosive Unloading of Gas in a Deep Water Riser When SOBM in Use; Colin P. Leach & Joseph R. Roche—1998 (The Paper Describes an Application for the Hydril Gas Handler, The Hydril GH 211-2000 Gas Handler is Depicted in Figure 1 of the Paper) (9 unnumbered pages).44Baker, Ron, "A Primer of Oilwell Drilling," Fourth Edition, Published Petroleum Extension Service, The University of Texas at Austin, Austin, Texas, in cooperation with International Association of Drilling Contractors Houston, Texas � 1979 (3 cover pages and pp. 42-49 re Circulation System).45Balluff Sensors Worldwide; Object Detection Catalog 08/09—Industrial Proximity Sensors for Non-Contact Detection of Metallic Targets at Ranges Generally under 50mm (2 inches); Linear Position and Measurement; Linear Position Transducers; Inductive Distance Sensors; Photoelectric Distance Sensors; Magneto-Inductive Linear Position Sensors; Magnetic Linear/Rotary Encoder System; printed Dec. 23, 2008 (8 pages).46Blowout Preventer Testing for Underbalanced Drilling by Charles R. "Rick" Stone and Larry A. Cress, Signa Engineering Corp., Houston, Texas (24 pages) Sep. 1997.47Bourgoyne, Darryl A.; Bourgoyne, Adam T.; Hannegan, Don; "A Subsea Rotating Control Head for Riserless Drilling Applications," IADC International Deep Water Well Control Conference, pp. 1-14, (Aug. 26-27, 1998) (see document T).48Boye, John: "Multi Purpose Intervention Vessel Presentation," M.O.S.T. Multi Operational Service Tankers, Weatherford International, Jan. 2004, 43 pages (� 2003).49Brochure, Lock down Lubricator System, Dutch Enterprises, Inc., "Safety with Savings" (cover sheet and 16 unnumbered pages); see above US Patent No. 4,836,289 referred to therein.50Brochure, Shaffer Type 79 Rotating Blowout Preventer, NL Rig Equipment/NL Industries, Inc., (6 unnumbered pages).51Brochure: "Inter-Tech Drilling Solutions, Ltd.'s RBOP(TM) Means Safety and Experience for Underbalanced Drilling," Inter-Tech Drilling Solutions Ltd./Big D Rentals & Sales (1981) Ltd. and Color Copy of "Rotating BOP" (2 unnumbered pages).52Brochure: "Inter-Tech Drilling Solutions, Ltd.'s RBOP™ Means Safety and Experience for Underbalanced Drilling," Inter-Tech Drilling Solutions Ltd./Big D Rentals & Sales (1981) Ltd. and Color Copy of "Rotating BOP" (2 unnumbered pages).53Bybee, Karen, "Offshore Applications of Underbalanced-Drilling Technology," Journal of Petroleum Technology, Cover Page and pp. 51-52, (Jan. 2004).54Bybee, Karen, "Offshore Applications of Underbalanced—Drilling Technology," Journal of Petroleum Technology, Cover Page and pp. 51-52, (Jan. 2004).55Cameron HC Collet Connector, � 1996 Cooper Cameron Corporation, Cameron Division (12 pages).56Coflexip Brochure; 1-Coflexip Sales Offices, 2-the Flexible Steel Pipe for Drilling and Service Applications, 3-New 5'' I.D. General Drilling Flexible, 4-Applications, and 5-Illustration (5 unnumbered pages).57Coflexip Brochure; 1-Coflexip Sales Offices, 2-the Flexible Steel Pipe for Drilling and Service Applications, 3-New 5″ I.D. General Drilling Flexible, 4-Applications, and 5-Illustration (5 unnumbered pages).58Colbert, John W., "John W. Colbert, P.E. Vice President Engineering Biographical Data," Signa Engineering Corp., 2 unnumbered pages (undated).59Composite Catalog, Hughes Offshore 1982/1983, Regan Products, � Copyright 1982 (Two cover sheets and 4308-27 thru 4308-43, and end sheet). See p. 4308-36 Type KFD Diverter.60Composite Catalog, Hughes Offshore 1986-87 Subsea Systems and Equipment, Hughes Drilling Equipment Composite Catalog (pp. 2986-3004).61D.O. Nessa, "Offshore underbalanced drilling system could revive field developments," World Oil Exploration Drilling Production, vol. 218, No. 7, Color pages of Cover Page and pp. 3, 61-64, and 66, Jul. 1997.62Dag Oluf Nessa, "Offshore underbalanced drilling system could revive field developments," World Oil, vol. 218, No. 10, Oct. 1997, 1 unnumbered page and pp. 83-84, 86, and 88.63DC 2-Wire Tubular Sensors, Balluff product catalog pp. 1.125-1.136 (12 pages) (no. date).64DC 3-/4-Wire Inductive Sensors, Balluff product catalog pp. 1.72-1.92 (21 pages).65Dietle, Lannie L., et al., Kalsi Seals Handbook, Document. 2137 Revision 1, � 1992-2005 Kalsi Engineering, Inc. Of Sugar Land, Texas USA; front and back covers and 164 total pages; in particular forward p. ii for "Patent Rights"; Appendix A-6 for Kalsi seal part No. 381-6- and A-10 for Kalsi seal part No. 432-32-. as discussed in U.S. Appl. No. 11/366,078 application at number paragraph 70 and 71.66E.Y. Nakagawa, H. Santos, J.C. Cunha and S. Shayegi, Planning of Deepwater Drilling Operations with Aerated Fluids, SPE 54283, 7 pages, (�1999, Society of Petroleum Engineers).67E.Y. Nakagawa, H.M.R. Santos and J.C. Cunha, Implementing the Light-Weight Fluids Drilling Technology in Deepwater Scenarios, 1999 LSU/MMS Well Control Workshop Mar. 24-25, 1999, 12 pages (1999).68EU 99908371.0-1266-US99/03888 European Search Report corresponding to US Patent No. 6,138,774 (3 pages) (Nov. 2, 2004).69EU Examination Report for 05270083.8-2315 corresponding toUS 2006/0108119 A1 published May 25, 2006 (11 pages) (May 10, 2006).70EU Examination Report for WO 00/906522.8-2315 corresponding to US Patent No. 6,263,982 (4 pages) (Nov. 29, 2004).71European Search Report for EP 05 27 0083, Application No. 05270083.8-2315, European Patent Office, Mar. 2, 2006 (5 pages).72Extended European search report R.44 EPC dated Oct. 9, 2007 for European Patent Application 07103416.9-2315 corresponding to U.S. Appl. No. 11/366,078, published as US-2006/0144622 A1, now US patent 7,836,946 (8 pages).73Feasibility Study of Dual Density Mud System for Deepwater Drilling Operations; Clovis A. Lopes & A.T. Bourgoyne, Jr.-1997 (Offshore Technology Conference Paper No. 8465); (pp. 257-266).74Feasibility Study of Dual Density Mud System for Deepwater Drilling Operations; Clovis A. Lopes & A.T. Bourgoyne, Jr.—1997 (Offshore Technology Conference Paper No. 8465); (pp. 257-266).75Field Exposure (As of Aug. 1998), Shaffer� A Varco Company (1 unnumbered page).76Fig. 10 and discussion in U.S. Appl. No. 11/366,078 application of Background of Invention.77Fig. 19 Floating Piston Drilling Choke Design: May of 1997.78Forrestt, Neil; Bailey, Tom; Hannegan, Don; "Subsea Equipment for Deep Water DrillingUSing Dual Gradient Mud System," SPE/IADC 67707, pp. 1-8, (�2001, SPE/IADC Drilling Conference).79Furlow, William; Shell's seafloor pump, solids removal key to ultra-deep, dual-gradient drilling (Skid ready for commercialization), Offshore World Trends and Technology for Offshore Oil and Gas Operations, Cover page, table of contents, pp. 54, 2 unnumbered pages, and 106 (Jun. 2001).80GB Search Report; International Application No. GB 0324939.8, 1 page (Jan. 21, 2004).81GB0324939.8 Examination Report corresponding to US Patent No. 6,470,975 (Mar. 21, 2006) (6 pages).82GB0324939.8 Examination Report corresponding to US Patent No. 6,470,975 Jan. 22, 2004 (3 pages).83General Catalog, 1970-1971, Vetco Offshore, Inc., Subsea Systems; cover page, company page and numbered pp. 4800, 4816-4818; 6 pages total, in particular see numbered p. 4816 for "patented" Vetco H-4 connectors.84General Catalog, 1972-73, Vetco Offshore, Inc., Subsea Systems; cover page; company page and numbered pp. 4498, 4509-4510; 5 pages total.85General Catalog, 1976-1977, Vetco Offshore, Inc., Subsea Drilling and Completion Systems; cover page and numbered pp. 5862-5863; 4 pages total.86General Catalog, 1982-1983, Vetco; cover page and numbered pp. 8454-8455, 8479; 4 pages total.87General Catalog, 974-75, Vetco Offshore, Inc.; cover page, company page and numbered pp. 5160, 5178-5179; 5 pages total.88Graphic: "Rotating Spherical BOP" (1 unnumbered page).89Gray, Kenneth; Dynamic Density Control Quantifies Well Bore Conditions in Real Time During Drilling; American Oil & Gas Reporter, Jan. 2009 (4 pages).90Hannegan, "Applications Widening for Rotating Control Heads," Drilling Contractor, cover page, table of contents and pp. 17 and 19, Drilling Contractor Publications Inc., Houston, Texas, Jul. 1996.91Hannegan, D. and Divine, R., "Underbalanced Drilling-Perceptions and Realities of Today's Technology in Offshore Applications," IDAC/SPE 74448, p. 1-9, (�2002, IADC/SPE Drilling Conference).92Hannegan, D. and Divine, R., "Underbalanced Drilling—Perceptions and Realities of Today's Technology in Offshore Applications," IDAC/SPE 74448, p. 1-9, (�2002, IADC/SPE Drilling Conference).93Hannegan, D.M.; Bourgoyne, Jr., A.T.: "Deepwater Drilling with Lightweight Fluids-Essential Equipment Required," SPE/IADC 67708, pp. 1-6 (�2001, SPE/IADC Drilling Conference).94Hannegan, D.M.; Bourgoyne, Jr., A.T.: "Deepwater Drilling with Lightweight Fluids—Essential Equipment Required," SPE/IADC 67708, pp. 1-6 (�2001, SPE/IADC Drilling Conference).95Hannegan, Don M. and Wanzer, Glen: "Well Control Considerations-Offshore Applications of Underbalanced Drilling Technology," SPE/IADC 79854, pp. 1-14, (�2003, SPE/IADC Drilling Conference).96Hannegan, Don M. and Wanzer, Glen: "Well Control Considerations—Offshore Applications of Underbalanced Drilling Technology," SPE/IADC 79854, pp. 1-14, (�2003, SPE/IADC Drilling Conference).97Hannegan, Don M., "Underbalanced Operations Continue Offshore Movement," SPE 68491, pp. 1-3, (�2001, Society of Petroleum Engineers, Inc.).98Hannegan, Don M.; Managed Pressure Drilling—A New Way of Looking at Drilling Hydraulics—Overcoming Conventional Drilling Challenges; SPE 2006-2007 Distinguished Lecturer Series presentation (29 pages).99Helio Santos, Email message to Don Hannegan, et al., 1 page (Aug. 20, 2001).100Helio Santos, Fabio Rosa, and Christian Leuchtenberg, Drilling and Aerated Fluid from a Floating Unit, Part 1: Planning, Equipment, Tests, and Rig Modifications, SPE/IADC 67748, 8 pages (�2001 SPE/IADC Drilling Conference).101Hole™ 2500 RCD Rotating Control Device web page and brochure, http://www.smith.com/hold2500; printed Oct. 27, 2004, 5 pages.102Hydril Blowout Preventers Catalog M-9402 D (44 pages) �2004 Hydrill Company LP; see annular and ram BOP seals on p. 41.103Hydril Compact GK� 71/16″-3000 & 5000 psi Annular Blowout Preventers, Catalog 9503B �1999 Hydril Company (4 pages).104Hydril GL series Annual Blowout Preventers (Patented-see Roche patents above), (cover sheet and 2 pages).105Hydril GL series Annual Blowout Preventers (Patented—see Roche patents above), (cover sheet and 2 pages).106Int'l Search Report for PCT/GB 00/00731 corresponding to US Patent No. 6, 470,975 (4 pages) (Jun. 27, 2000).107Int'l. Preliminary Examination Report for PCT/GB 00/00731 corresponding to US Patent No. 6,470,975 (7 pages) (Dec. 14, 2000).108Int'l. Search Report for PCT/GB 00/00731 corresponding to US :Patent No. 6,470,975 (Jun. 16, 2000) (2 pages).109Kotow, Kenneth J.; Pritchard, David M.; Riserless Drilling with Casing: A New Paradigm for Deepwater Well Design, OTC-19914-PP, �2009 Offshore Technology Conference, Houston, TX May 4-7, 2009 (13 pages).110Lage, Antonio C.V.M.; Santos, Helio; Silva, Paulo R.C.; "Drilling With Aerated Drilling Fluid From a Floating Unit Part 2: Drilling the Well," Society of Petroleum Engineers, SPE 71361, pp. 1-11 (Sep. 30-Oct. 3, 2001)(see document BBB).111Liquid Flowmeters, Omega.com website; printed Jan. 26, 2009 (13 pages).112Managed Pressure Drilling in Marine Environments, Don Hannegan, P.E.; Drilling Engineering Association Workshop, Moody Gardens, Galveston, Jun. 22-23, 2004; �2004 Weatherford, 28 pages.113Medley, George; Moore, Dennis; Nauduri, Sagar; Signa Engineering Corp.; SPE/IADC Managed Pressure Drilling & Underbalanced Operations (PowerPoint presentation; 22 pages).114MicroPatent� list of patents citing US Patent No. 3,476,195, printed on Jan. 24, 2003.115Murphy, Ross D. and Thompson, Paul B., "A drilling contractor's view of underbalanced drilling," World Oil Magazine, vol. 223, No. 5, 9 pages (May 2002).116Nakagawa, Edson Y., Santos, Helio and Cunha, J.C., "Application of Aerated-Fluid Drilling in Deepwater," SPE/IACDC 52787 Presented by Don Hannegan, P.E., SPE � 1999 SPE/IADC Drilling Conference, Amsterdam, Holland, Mar. 9-11, 1999 (5 unnumbered pages).117National Academy of Sciences-National Research Council, "Design of a Deep Ocean Drilling Ship," Cover Page And pp. 114-121. Undated but cited in above US Patent No. 6,230,824B1.118National Academy of Sciences—National Research Council, "Design of a Deep Ocean Drilling Ship," Cover Page And pp. 114-121. Undated but cited in above US Patent No. 6,230,824B1.119Nessa, D.O. & Tangedahl, M.L. & Saponia, J: Part 1: "Offshore underbalanced drilling system could revive field developments," World Oil, vol. 218, No. 7, Cover Page, 3, 61-64 and 66 (Jul. 1997); and Part 2: "Making this valuable reservoir drilling/completion technique work on a conventional offshore drilling platform." World Oil, vol. 218 No. 10, Cover Page, 3, 83, 84, 86 and 88 (Oct. 1997) (see 5A, 5G above and 5I below).120Netherlands Search Report for NL No. 1026044, dated Dec. 14, 2005 (3 pages).121NL Examination Report for WO 00/52299 corresponding to this US S/N 10/281,534 (3 pages) (Dec. 19, 2003).122NO S/N 20003950 Examination Report w/one page of English translation corresponding to US Patent No. 6,138,774 (3 pages) (Nov. 1, 2004).123NO S/N 20013952 Examination Report w/two pages of English translation corresponding to US Patent No. 6,263,982 (4 pages) (Jul. 2, 2005).124NO S/N 20013953 Examination Report corresponding to US Patent No. 6,470,975 w/one page of English translation (3 pages) (Apr. 29, 2003).125Office Action from the Canadian Intellectual Property Office dated Nov. 13, 2008 for Canadian Application No. 2,580,177 corresponding to U.S. Appl. No. 11/366,078, published as US-2006/0144622 A1, now US Patent No. 7,836,946 (3 pages).126Offshore-World Trends and Technology for Offshore Oil and Gas Operations, Mar. 1998, Seismic: Article entitled, "Shallow Flow Diverter JIP Spurred by Deepwater Washouts" (3 pages including cover page, table of contents and p. 90).127Offshore—World Trends and Technology for Offshore Oil and Gas Operations, Mar. 1998, Seismic: Article entitled, "Shallow Flow Diverter JIP Spurred by Deepwater Washouts" (3 pages including cover page, table of contents and p. 90).128Other Hydril Product Information (The GH Gas Handler Series Product is Listed), � 1996, Hydril Company (Cover sheet and 19 pages).129Partial European search report R.46 EPC dated Jun. 27, 2007 for European Patent Application EP07103416.9-2315 corresponding to U.S. Appl. No. 11/366,078, published as US 2006/0144622 A1, now US Patent 7,836,946 (5 pages).130PCT Search Report, International Application No. PCT/EP2004/052167, 4 pages (Date of Completion Nov. 25, 2004).131PCT Search Report, International Application No. PCT/GB00/00731, 3 pages (Date of Completion Jun. 16, 2000).132PCT Search Report, International Application No. PCT/US99/06695, 4 pages (Date of Completion May 27, 1999).133PCT Written Opinion of the International Searching Authority, International Application No. PCT/EP2004/052167, 6 pages.134PCT/GB00/00726 International Search Report corresponding to US Patent No. 6,263,982 (3 pages (Mar. 2, 1999).135PCT/GB00/00726 Int'l. Preliminary Examination Report corresponding to US Patent No. 6,263,982 (10 pages) (Jun. 26, 2001).136PCT/GB00/00726 Written Opinion corresponding to US Patent No. 6,263,982 (7 pages) (Dec. 18, 2000).137PCT/GB2008/050239 (corresponding to US2008/0210471 A1) Annex to Form PCT/ISA/206 Communication Relating to the Results of the Partial International Search dated Aug. 26, 2008 (4 pages).138PCT/GB2008/050239 (corresponding to US2008/0210471 A1) International Search Report and Written Opinion of the International Searching Authority (16 pages).139PCT/US99/03888 Notice of Transmittal of International Preliminary Examination Report corresponding to US Patent No. 6,138,774 (15 pages) (Jun. 12, 2000).140PCT/US99/03888 Written Opinion corresponding to US Patent No. 6,138,744 (5 pages) (Dec. 21, 1999).141PCT/US990/03888 Notice of Transmittal of International Search Report corresponding to US Patent No. 6,138,774 (6 pages) (Aug. 4, 1999).142Performance Drilling by Precision Drilling. A Smart Equation, Precision Drilling, �2002 Precision Drilling Corporation; 12 pages, in particular see 9th page for "Northland's patented RBOP. . .".143Press Release, "Stewart & Stevenson Introduces First Dual Gradient Riser," Stewart & Stevenson, http:/www.ssss/com/ssss/20000831.asp, 2 pages (Aug. 31, 2000).144Press Release: "Stewart & Stevenson introduces First Dual Gradient Riser," Stewart & Stevenson, http:www/ssss/com/ssss/20000831.asp, 2 pages (Aug. 31, 2000).145Rach, Nina M., "Underbalanced near-balanced drilling are possible offshore," Oil & Gas Journal, Color Copies, pp. 39-44, (Dec. 1, 2003).146Rehm, Bill, "Practical Underbalanced Drilling and Workover," Petroleum Extension Service, The University of Texas at Austin Continuing & Extended Education, cover page, title page, copyright page and pp. 6-1 to 6-9, 7-1 to 7-9 (2002).147Rehm, Bill, "Practical Underbalanced Drilling and Workover," Petroleum Extension Service, The University of Texas at Austin Continuing & Extended Education, Cover page, title page, copyright page, and pp. 6-6, 11-2, 11-3, G-9, and G-10 (2002).148Riserless drilling: circumventing the size/cost cycle in deepwater- Conoco, Hydril project seek enabling technologies to drill in deepest water depths economically, May 1986 Offshore Drilling Technology (pp. 49, 50, 52, 53, 54 and 55).149Riserless drilling: circumventing the size/cost cycle in deepwater— Conoco, Hydril project seek enabling technologies to drill in deepest water depths economically, May 1986 Offshore Drilling Technology (pp. 49, 50, 52, 53, 54 and 55).150Rowden, Michael V.: Advances in riserless drilling pushing the deepwater surface string envelope (Alternative to seawater, CaCl2 sweeps); Offshore World Trends and Technology for Offshore Oil and Gas Operations, Cover pages, table of contents, pp. 56, 58, and 106 (Jun. 2001).151RPM System, 3000™ Rotating Blowout Preventer: Setting a New Standard in Well Control, Weatherford, Underbalanced Systems: �2002-2005 Weatherford; Brochure #333.01, 4 pages.152Secure Drilling Well Controlled, Secure Drilling™ System using Micro-Flux Control Technology, �2007 Secure Drilling (12 pages).153Selecting Position Transducers: How to Choose Among Displacement Sensor Technologies; How to Choose Among Draw Wire, LVDT, RVDT, Potentiometer, Optical Encoder, Ultrasonic, Magnetostrictive, and Other Technologies; �2009 M-I, LLLC �1996-2010 Space Age Control, Inc., printed Feb. 18, 2010 (6 pages).154Shaffer, A Varco Company, (Cover page and pp. 1562-1568).155Shaffer, A Varco Company: Pressure Control While Drilling System, http:/www.tulsaequipm.com; printed Jun. 21, 2004; 2 pages.156Smith Services product details for Rotating Control Device—RDH 500� printed Nov. 24, 2008 (4 pages).157Super Autochoke—Automatic Pressure Regulation Under All Conditions �2009 M-I, LLC; MI Swaco website; printed Apr. 2, 2009 (1 page).158Supplementary European Search Report No. EP 99908371, 3 pages (Date of Completion Oct. 22, 2004).159Tangedahl, M.J., et al. "Rotating Preventers: Technology for Better Well Control," World Oil, Gulf Publishing Company, Houston, TX, US, vol. 213, No. 10, 10/1992, (Oct. 1, 1992) numbered pp. 63-64 and 66 (3 pages) XP 000288328 ISSN: 0043-8790 (see YYYY, 5X above).160Tangedahl, M.J., et al., "Rotating Preventers: Technology for Better Well Control," World Oil, Gulf Publishing Company, Houston, TX, US, vol. 213, No. 10, Oct. 1992, numbered pp. 63-64 and 66 (3 pages).161The LSU Petroleum Engineering Research & Technology Transfer Laboratory, 10-rate Step Pump Shut-down and Start-up Example Procedure for Constant Bottom Hole Pressure Manage Pressure Drilling Applications (8 pages).162The Modular T BOP Stack System, Cameron Iron Works� 1985 (5 pages).163Turck Works Industrial Automation; Factor 1 Sensing for Metal Detection (2 pages) (no. date).164U.S Appl. No. 60/122,530, Priority Claimed in US Patent No. 6,470,975B1, filed Mar. 2, 1999.165U.S. Appl. No. 60/079,641, Abandoned, but Priority Claimed in above US Patent Nos. 6,230,824B1 and 6,102,673 and PCT WO 99/50524, filed Mar. 27, 1998.166UK Examination Report for Application No. GB 0325423.2 (corresponding to above 5Z) (4 pages).167UK Search Report for Application No. GB 0325423.2, searched Jan. 30, 2004 corresponding to above US Patent No. 7,040,394 (one page).168United States Department of the Interior Minerals Management Service Gulf of Mexico OCS Region NTL No. 2008-G07; Notice to Lessees and Operators of Federal Oil, Gas, and Sulphur Leases in the Outer Continental Shelf, Gulf of Mexico OCS Region, Managed Pressure Drilling Projects; Issue Date: May 15, 2008; Effective Date: Jun. 15, 2008; Expiration Date: Jun. 15, 2013 (9 pages).169US 6,708,780, 11/2001, Bourgoyne et al. (withdrawn)170US Provisional Patent Application No. 60/079,641, Mudlift System for Deep Water Drilling, filed Mar. 27, 1998, abandoned, but priority claimed in above US 6,230,824 B1 and 6,102,673 and PCT WO-99/50524 (54 pages).171US Provisional Patent Application No. 60/122,530, Concepts for the Application of Rotating Control Head Technology to Deepwater Drilling Operations, filed Mar. 2, 1999, abandoned, but priority claimed in above US 6,470,975 B1 (54 pages).172Vetco Gray Capital Drilling Equipment KFDJ and KFDJ Model "J" Diverters (1 page) (no date).173Vetco Gray Product Information CDE-PI-0007 dated Mar. 1999 for 59.0″ Standard Bore CSO Diverter (2 pages) �1999 By Vetco Gray Inc.174Washington Rotating Control Heads, Inc. Series 1400 Rotating Control Heads ("Shorty") printed Nov. 21, 2008 (2 pages).175Weatherford "Real Results Rotating Control Device Resolves Mud Return Issues in Extended-Reach Well, Saves Equipment Costs and Rig Time" �2007 Weatherford and "Rotating Control Device Ensures Safety of Crew Drilling Surface-Hole Section" � 2008 Weatherford (2 pages).176Weatherford Controlled Pressure Drilling Model 7800 Rotating Control Device � 2007 Weatherford(5 pages).177Weatherford Controlled Pressure Drilling Williams� Rotating Marine Diverter Insert (2 pages).178Weatherford Controlled Pressure Drilling� and Testing Services Williams� Model 8000/9000 Conventional Heads � 2002-2006 Weatherford(2 pages).179Weatherford Drilling & Intervention Services Underbalanced Systems RPM System 3000™ Rotating Blowout Preventer, Setting a New Standard in Well Control, An Advanced Well Control System for Underbalanced Drilling Operations, Brochure #333.00, �2002 Weatherford (4 pages).180Williams Rotating Control Heads, Reduce Costs Increase Safety Reduce Environmental Impact (4 pages).181Williams Rotating Control Heads, Reduce Costs Increase Safety Reduce Environmental Impact, 4 pages, (� 1995).182Williams Tool Co., Inc. 19 page brochure � 1991 Williams Tool Co., Inc. (19 pages).183Williams Tool Co., Inc. Instructions, Assemble & Disassemble Model 9000 Bearing Assembly (cover page and 27 numbered pages).184Williams Tool Co., Inc. Rotating Control Heads and Strippers for Air, Gas, Mud, and Geothermal Drilling Worldwide-Sales Rental Service, � 1988 (19 pages).185Williams Tool Co., Inc. Rotating Control Heads and Strippers for Air, Gas, Mud, and Geothermal Drilling Worldwide—Sales Rental Service, � 1988 (19 pages).186Williams Tool Co., Inc. Rotating Control Heads Making Drilling Safer While Reducing Costs Since 1968, �1989 (4 pages).187Williams Tool Co., Inc. Sales-Rental-Service, Williams Rotating Control Heads and Strippers for Air, Gas, Mud, and Geothermal Drilling, � 1982 (7 pages).188Williams Tool Co., Inc. Technical Specifications Model for the Model 7100, (3 pages).189Williams Tool Co., Inc. Website, "Model 7100," (3 pages).190Williams Tool Co., Inc. Website, Underbalanced Drilling (UBD), The Attraction of UBD (2 pages).191Williams Tool Co., Inc. Website,. "Applications, Where Using a Williams Rotating Control Head While Drilling is a Plus" (2 pages).192Williams Tool Co., Inc., Rotating Control Heads and Strippers for Air, Gas, Mud, Geothermal and Pressure Drilling, � 1991 (19 pages).193Williams Tool Company Inc., "RISERCAP(TM): Rotating Control Head System For Floating Drilling Rig Applications," 4 unnumbered pages, (� 1999 Williams Tool Company, Inc.).194Williams Tool Company Inc., "RISERCAP™: Rotating Control Head System For Floating Drilling Rig Applications," 4 unnumbered pages, (� 1999 Williams Tool Company, Inc.).195Williams Tool Company Inc., "Williams Tool Company Introduces the . . . Virtual Riser(TM)," 4 unnumbered pages, (�1998 Williams Tool Company, Inc.).196Williams Tool Company Inc., "Williams Tool Company Introduces the . . . Virtual Riser™," 4 unnumbered pages, (�1998 Williams Tool Company, Inc.).197Williams Tool Company, Inc. International Model 7000 Rotating Control Head, 1991 (4 pages).198Williams Tool Company-Home Page-Under Construction Williams Rotating Control Heads (2 pages); Seal-Ability for the pressures of drilling (2 pages); Williams Model 7000 Series Rotating Control Heads (1 page); Williams Model 7000 & 7100 Series Rotating Control Heads (2 pages); Williams Model IP1000 Rotating Control Head (2 pages); Williams Conventional Models 8000 & 9000 (2 pages); Applications Where Using a Williams rotating control head while drilling is a plus (1 page); Williams higher pressure rotating control head systems are Ideally Suited for New Technology Flow Drilling and Closed Loop Underbalanced Drilling (UBD) Vertical and Horizontal (2 pages); and How to Contact US (2 pages).199Williams Tool Company—Home Page—Under Construction Williams Rotating Control Heads (2 pages); Seal-Ability for the pressures of drilling (2 pages); Williams Model 7000 Series Rotating Control Heads (1 page); Williams Model 7000 & 7100 Series Rotating Control Heads (2 pages); Williams Model IP1000 Rotating Control Head (2 pages); Williams Conventional Models 8000 & 9000 (2 pages); Applications Where Using a Williams rotating control head while drilling is a plus (1 page); Williams higher pressure rotating control head systems are Ideally Suited for New Technology Flow Drilling and Closed Loop Underbalanced Drilling (UBD) Vertical and Horizontal (2 pages); and How to Contact US (2 pages).Referenced byCiting PatentFiling datePublication dateApplicantTitleUS9038729 *Sep 28, 2011May 26, 2015Smith International, Inc.Adaptor flange for rotary control deviceUS9316319 *Nov 30, 2010Apr 19, 2016Kalsi Engineering, Inc.Pressure-balanced floating seal housing assembly and methodUS9359853Sep 15, 2011Jun 7, 2016Weatherford Technology Holdings, LlcAcoustically controlled subsea latching and sealing system and method for an oilfield deviceUS20110127725 *Nov 30, 2010Jun 2, 2011Kalsi Engineering, Inc.Pressure-balanced floating seal housing assembly and methodUS20120073113 *Sep 28, 2011Mar 29, 2012Smith International, Inc.Adaptor flange for rotary control device* Cited by examinerClassifications U.S. Classification166/84.2, 166/387International ClassificationE21B19/24Cooperative ClassificationF16J15/324, E21B33/085, F16K41/046, E21B36/001, E21B47/10European ClassificationE21B33/08B, E21B34/16, E21B36/00B, F16J15/32C, F16K41/04B2Legal EventsDateCodeEventDescriptionOct 22, 2010ASAssignmentOwner name: WEATHERFORD/LAMB, INC., TEXASFree format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:BAILEY, THOMAS F.;CHAMBERS, JAMES W.;HANNEGAN, DON M.;AND OTHERS;REEL/FRAME:025183/0117Effective date: 20060302Oct 8, 2014FPAYFee paymentYear of fee payment: 4Dec 4, 2014ASAssignmentOwner name: WEATHERFORD TECHNOLOGY HOLDINGS, LLC, TEXASFree format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:WEATHERFORD/LAMB, INC.;REEL/FRAME:034526/0272Effective date: 20140901RotateOriginal ImageGoogle Home - Sitemap - USPTO Bulk Downloads - Privacy Policy - Terms of Service - About Google Patents - Send FeedbackData provided by IFI CLAIMS Patent Services