southwest mud pump liner pressure ratings manufacturer

22 4020-73 CYLINDER HEAD STUD (WITH SW PART# HHN1500-8 1-1/2-8 HEAVY HEX NUT) 30 *CONTINENTAL EMSCO STYLE PARTS ARE OPTIONAL ON THIS MUD PUMP SEE PAGE 3 FOR ASSEMBLY DRAWING

The present invention relates generally to mud pumps and particularly relates to a system and apparatus for aligning and securing the cylinder liners of such pumps to their respective pumping modules. More particularly, the present invention relates to a hydraulic retention system and apparatus for aligning and securing the cylinder liner. Still more particularly, the system and apparatus include a positive metal to metal locking feature.

In extracting hydrocarbons, such as oil and gas, from the earth, on land and subsea, it is common to drill a wellhole into the earth formation containing the hydrocarbons. A drill bit is attached to a drill string, including joined sections of drill pipe, suspended from a drilling rig. As the drill bit rotates, the hole deepens and the string is lengthened by attaching additional sections of drill pipe. During drilling operations, drilling fluid, or “mud” as it is also known, is pumped down through the drill pipe and into the hole through the drill bit. Drilling fluids are used to lubricate the drill-bit and keep it cool. The drilling mud also cleans the bit, and balances pressure by providing weight downhole, as well as bringing up sludge and cuttings from the drilling process to the surface.

Slush or mud pumps are commonly used for pumping the drilling mud. Because of the need to pump the drilling mud through several thousand feet of drill pipe, such pumps typically operate at very high pressures. Moreover, it is necessary for the mud to emerge from the drill bit downhole at a relatively high velocity to lubricate and cool the bit and to effectively remove cuttings from the hole. Lastly, the pressure generated by the mud pump contributes to maintaining a predetermined total downhole pressure, which is necessary to prevent well blowouts.

The pistons and cylinders used for such mud pumps are susceptible to a high degree of wear during use because the drilling mud is relatively dense and has a high proportion of suspended abrasive solids. As the cylinder becomes worn, the small annular space between the piston head and the cylinder wall increases substantially and sometimes irregularly. This decreases the efficiency of the pump. To reduce the effect of this wear, the cylinder typically is provided with a replacable cylinder liner.

It is the usual practice to replace the cylinder liner at end of its useful life. The pump cylinder liner in a duplex pump typically has an average life of 1200 to 1500 pump hours, or about 90 to 100 days. A duplex pump has two reciprocating pistons that each force fluid into a discharge line. The average life of the cylinder liners in a triplex pump is about 500 to 900 hours or about 50 to 60 days of service life at a normal duty cycle. Triplex reciprocating pumps have three pistons that force fluid into a discharge line. These fluid pumps can be single acting, in which fluid is discharged on alternate strokes, or double acting, in which each stroke discharges fluid.

In the course of installing or replacing a cylinder liner, the cylinder liner may become misaligned. Misaligned contact between the metal piston head and the cylinder creates considerable friction, abrasion, and heat. This, in turn, causes the cylinder liner, as well as other various pump parts, such as seals, to be susceptible to an increased rate of wear. In some cases, the frictional forces may even cause the seal to detach from the piston. For these reasons, the alignment of the cylinder liner of such pumps is critical.

Further, changing a cylinder liner in a mud pump is typically a difficult, dirty, and heavy job. Still further, because drilling rig time is very expensive, frequent replacement of cylinder liners causes considerable inconvenience if the system and apparatus for releasing the old cylinder liners and fitting the replacement cylinder liners are slow or difficult to operate. Thus, it is important that the system and method for aligning and securing the cylinder liners may be implemented without undue effort and down-time.

Some original pump designs include a large threaded sledge hammer nut that is hammered on and off to hold the liner in place. Such a system for securing cylinder liners to respective pumping modules is difficult to operate for a variety of reasons, including the involvement of heavy components, the handling of which may be dangerous for operators. These types of systems require considerable strength, skill and reliability of operators, together with the use of heavy tools in confined spaces. Thus, it is difficult to apply a specified torque to within a desired preset tolerance. Further, the securing force is dependent on the extent of wear and the general condition of the securing components.

There are several alternative ways to attach cylinder liners to their respective pumping modules and these may vary according to make of pump in which they are used. One embodiment presently known employs a tapered concentric clamp, while another uses a concentric screw clamping arrangement. The tapered clamp is susceptible to corrosion and wear, which diminish its effectiveness. Other pump designs require large wrenches or impact socket tools to remove large nuts from studs so as to release the retainer. Not only is this not an precise way to load the liner seal, but in some models the rotation effect can dislodge and fail the seal mechanism. In all of these systems, the force securing the cylinder liner is difficult to control, causing the cylinder liner to be susceptible to misalignment.

In still another known design, a replacement device involves removal of some of the original parts and uses hydraulics and belville washers to load, hold, and restrain the liner. This system relies on a spring lock, and therefore the securing force is dependent on the ability of the spring to retain its stiffness against the securing components. In addition, it relies on nuts secured on studs spaced about the circumference of the cylinder. Thus, this system causes the cylinder liner to be susceptible to misalignment arising from unequal securing forces at each stud, which can be caused by unequal tightening of each nut.

Notwithstanding the above teachings, there remains a need to develop a new and improved system and apparatus for retaining and replacing a cylinder liner which overcomes the foregoing difficulties while providing more advantageous overall results.

The present invention features a hydraulic retention system that includes a hydraulic body attached to the pump module. The body surrounds a hydraulic ram, which bears on the cylinder liner and is adapted to impart a securing force to the cylinder liner. The ram has a secured position achieved upon pressurization of hydraulic fluid contained in a chamber defined between the body and the ram. In the absence of hydraulic pressure, the ram is mechanically held in the secured position by a locking member that engages the body.

The present system provides a metal to metal lock and promotes alignment. The present system makes the task of changing liners easier and much safer due to the lack of a need for high power or dangerous tools, such as sledge hammers. The hydraulic hand pump utilized in the present system is easy and safe, and features precise securing forces. The liner alignment is a advantage of these machines and this design is an improvement on previously known designs.

The design of mud pump modules is known to one of ordinary skill in the art, for example as disclosed in U.S. Pat. Nos. 4,486,938 and 5,616,009, each hereby incorporated herein by reference. Referring to FIG. 1, an exemplary prior art mud pump 10 includes retention member 12. Retention member 12 preferably comprises a substantially cylindrical retention sleeve 14 that includes a front face 16 and an outer surface 18. Retention member 12 optionally includes a centering sleeve (not shown) lining the inner surface of the retention sleeve 14. A cylinder liner 20 is disposed within retention member 12, preferably contacting the inner surface of retention member 12. A wear plate 22 provides a renewable surface for liner 20. A liner seal 26 is preferably positioned between end 24 of cylinder liner 20 and wear plate 22. A piston 28 is disposed within liner 20 and is connected to a rod 30 which, in turn, is connected to a slider crank mechanism (not shown) driven by an electric motor or engine (not shown). In operation, the piston 28 reciprocates within liner 20. The orientation of the piston 28 may be reversed from that shown in FIG. 1, depending on the configuration of the pump. Between the cylinder liner 20 and the piston 28 is a small annular space 32. The piston 28 includes a piston head 34 having an annular seal 36 is disposed thereon. Seal 36 contacts the inside of cylinder liner 20. Pump fluid is located in chamber 38 defined by liner 20, piston 28, and wear plate 22. Chamber 38 is in fluid communication with a passageway (not shown) through a pump manifold (not shown). The pump fluid is pressurized by the movement of the piston 28 within the liner 20. Seal 36 is provided to seal the annular space 32 and thereby prevent the fluid from leaking behind piston head 34. Seal 36 also preferably helps keep the piston 28 centered so as to maintain the annular space 32 separating piston 28 from cylinder liner 20. In operation, piston 28 and liner 20 will become worn, particularly if piston 28 and liner 20 come into contact as a result of misalignment. At some point, the degree of wear will be so great that operation of the pump will be impaired. For this reason, it is desirable to have a liner retention system that is reliable and easy to install, operate, and remove.

Referring now to FIG. 2, a preferred hydraulic retention system 40 that may be used to replace prior liner retention systems in known mud pumps, such as described above, includes a slidable member 42, a pair of seals 44, 46, a locking member 48, a body 50 and a retention member 52. A lug adapter 54 preferably is disposed between retention member 52 and body 50, and attaches body 50 to retention member 52. Slidable member 42 is in slidable contact with body 50 and has an unsecured position and a secured position. The slidable member 42 is shown in the unsecured position in FIG. 2. Seals 44, 46 are disposed around slidable member 42 and seal the interface between slidable member 42 and body 50. The first seal 44 is located inwardly of shoulder 56 and the second seal 46 is located outwardly of a shoulder 56.

Slidable member 42 is preferably in the form of a hydraulic ram 43. Hydraulic rams are known in the art, and may take a number of forms. In a preferred embodiment ram 43 is disposed around liner 58, and preferably extends circumferentially around the liner 58. Ram 43 includes a back face 62, an outer surface 64, and an inner surface 66. A gap 68 is defined between back face 62 and the front face 70 of retention member 52. Preferably, gap 68 is from about ⅛ to about {fraction (1/16)} inch wide when the slidable member 42 is in the unsecured position. When the slidable member 42 is in the secured position (not shown) gap 68 is smaller. Outer surface 64 includes outer annular shoulder 56. Inner surface 66 includes a first diameter portion 74, a second, smaller diameter portion 76, and an inner annular shoulder 78 therebetween. Inner annular shoulder 78 engages a corresponding lip 80 on liner 58. This orientation of the mating surface 78 has the advantage that force transmitted between ram 43 and liner 58 is substantially axial, compelling liner 58 axially towards the module. This has the advantage of aiding the desired alignment of liner 58. Liner 58 is preferably made from metal, as is ram 43. Further, mating surface 78 is preferably in positive metal-to-metal contact with a portion of the surface of the liner 58.

Still referring to FIG. 2, body 50 is disposed around lug adapter 54, ram 43, and locking member 48. Body 50 includes a lug 82 engaging lug adapter 54, is in sealing contact with ram 43, and engages the locking member 48. Further, body 50 includes an inner annular shoulder 84, a locking surface 86 having threads 88, a tool recess 90, a first fluid passage 92, and a second fluid passage 94. Shoulder 84 of body 50 is offset from shoulder 78 of ram 43, so that a chamber 96 is defined therebetween. Passage 92 extends through body 50 between its outer surface to its inner surface. Passage 92 includes an inner opening 98 and an outer portion 100. Inner opening 98 is in fluid communication with chamber 96 and outer portion 100 is adapted to receive a quick hose coupling 102, which is in turn attached to a pump (not shown). Second passage 94 is also in fluid communication with chamber 96 and is preferably positioned about 180 degrees from passage 92. Passage 94 is adapted to received a rupture disc 104. As mentioned below, threads 88 engage threads 106 of the locking member 48.

Chamber 96 is defined between shoulder 84 of body 50 and shoulder 56 of ram 43 and between slidable member 42 and body 50 and is adapted to receive retention hydraulic fluid, which may be pressurized by any suitable means, such as a hand pump. Seals 44, 46 prevent leakage of hydraulic fluid from chamber 96. Pressurization of the retention hydraulic fluid causes movement of slidable member 42 between the unsecured and secured positions. Locking member 48 has a locked and an unlocked position. In the locked position, the locking member 48 holds slidable member 42 in the secured position. When the slidable member 42 is in the secured position, a liner 58 in contact with slidable member 42 is held securely against the liner seal (not shown) between liner 58 and a wear plate (not shown). In addition to securing the liner 58, slidable member 42 energizes the liner seal as the liner 58 is compressed against the liner seal.

Referring now to FIG. 4, in another preferred embodiment, slidable assembly 42 includes a ram 136 and a bushing 138. Bushing 138 is disposed between slidable assembly 42 and liner 58. Bushing 138 lines a portion of the inner surface of ram 136. Ram 136 includes an inner surface 146 that contacts bushing 140 and includes an annular shoulder 148. Bushing 138 includes an outer surface 150 having a shoulder 152. Bushing 138 further includes an inner surface 154 that includes at least one radial mating surface 156. Shoulder 148 of ram 136 bears on shoulder 152 of bushing 138, while mating surface 156 bears on corresponding mating surface 158 of liner 144. In this manner, bushing 140 is adapted to transmit a longitudinal force from ram 136 to liner 58. Mating surfaces 156,158 are preferably in positive metal-to-metal contact.

Upon pressurization of fluid disposed in chamber 96, slidable member 42 slides longitudinally between an unsecured position shown in FIGS. 2 and 4 and a secured position (not shown). In the secured position, the width of gap 68 is reduced and cylinder liner 58 is compressed against the liner seal.

The locking member 48 adjusts between an unlocked position, shown in FIGS. 2 and 4, and a locked position (not shown). When locking member 48 is in its unlocked position, slidable assembly 42 is free to slide between the unsecured and secured positions. When slidable assembly 42 is in its secured position, locking member 48 can be set in its locked position. When the locking member 48 is in the locked position, the fluid in chamber 96 can be depressurized and slidable assembly 42 is mechanically held in the secured position by the locking member 48. An advantage of the preferred embodiment is that locking member 48 can be adjusted by hand. Further, the present hydraulic retention system provides the advantage of installing and aligning the liner with a precise, circumferentially uniform hydraulic force and retaining the liner in secure alignment.

Referring to FIGS. 2 and 4, the present hydraulic retention system 40 operates as follows. When slidable member 42 begins in the unsecured position, application of pressure to the retention hydraulic fluid causes a longitudinal force to be applied to slidable member 42, compelling it toward to the pump module. The slidable member 42 in turn transmits a force to liner 58, compelling liner 58 towards the pump module. Locking member 48 can be rotated from the unlocked position to the locked position.

In the secured position, slidable member 42 applies a retaining force to the liner 58. When it is desired to release slidable member 42 from its secured position, an application of pressure to the retention fluid balances any return force from slidable member 42 against locking member 48, allowing locking member 48 to be rotated from the locked position to the unlocked position. As the fluid pressure in chamber 96 is released, the energy stored in the compressed liner 58, is transmitted to the slidable member 42, which in turns slides toward the locking member 48.

The hydraulic retention system is installed according to the following preferred method. The liner adapter is threaded into a pump module until mated against the counter bore of the pump module. The lug adapter is threaded onto the liner adapter until the face of the lug adapter is flush with the face of the liner adapter, preferably within {fraction (1/32)} inch, and until the lug recess is in the top position. Set screws 120 are tightened, preferably to about 25 ft. pounds. Set screws prevent the lug adapter from rotating. The liner is installed with a gasket, with the gasket securely mated against the wear plate. The lug bushing 140 is installed onto the liner. The width of the gap between the back face 81 of the lug bushing 140 and the front face 114 of the lug adapter 54 is preferably from ⅛ to {fraction (3/16)} inches. A hand pump is preferably connected to the quick connect before the hydraulic retention system is installed, to allow free movement of the ram. The hydraulic retention system is then installed onto lug bushing 140 and onto lug adapter 54. One lug is preferably aligned with the T-handle slot. The hydraulic retention system is pushed forward until the lug clears the lug recess. Then, the hydraulic retention system is rotated clockwise, approximately 25 degrees, until the lug stops against the lug recess shoulder, and preferably the T-handle is in the top position.

Preferably, the hydraulic retention system is operated according to the following method. For first time use, the air is purged from the hydraulic retention system. Preferably, purging is accomplished by removing the pipe plug while using a hand pump, until the hydraulic fluid is present. Then the pipe plug is reinstalled and tightened. The pipe plug is preferably tightened to about 15 ft. lbs. The hydraulic retention system is then ready for use. In use, the hydraulic retention system is pressured up to a rated system pressure of about 5000-10,000 psi. The rupture disk is preferably set for about 20% above the rated system pressure, within a tolerance of ±200 psi. If the hydraulic retention system is overpressured, the rupture disk will fail, causing pressure loss. Pressure is applied to the hydraulic retention system with any suitable pump. After the hydraulic retention system is pressurized, the ram slides until the back face of the ram contacts the front face of the lug adapter. Sliding of the ram imparts a force to the cylinder liner, compelling the cylinder liner toward the pumping module and compressing the cylinder liner against the gasket. Preferably, the force is imparted via the bushing. In particular, the ram imparts a force to the bushing and the bushing in turn imparts a force to the cylinder liner. Once the cylinder liner is held in place by the fluid pressure, the locking ring can be tightened snugly by hand. An advantage of the present preferred embodiment is the enablement of the hand tightening of the locking ring. After the locking ring has been tightened, the fluid pressure is released, and the quick connect hose fitting can be disconnected.

The hydraulic retention system is removed according to the following preferred method. The pump is preferably connected throughout the removal procedure to allow free movement of the ram. The hydraulic retention system is pressured up to a maximum of the rated system pressure. After the hydraulic retention system is pressurized up, the locking ring is loosened at least two complete turns. After the locking ring is loosened, fluid pressure is released. Optionally, the front face of the locking ring can be tapped with a soft face hammer, thus jarring the components loose. The hydraulic retention system is rotated by hand until the lug comes in contact with lug opening shoulder. The hydraulic retention system is then removed. The lug bushing is then removed.

It is understood that although the invention is described with particular reference to a pump piston used with slush or mud pumps, it will be recognized that the hydraulic rentention system may be used or adapted to use for retaining other mud pump parts, such as valve pot covers. Further, it will be recognized that mud pumps are exemplary of reciprocating or positive displacement pumps and certain features thereof may be used or adapted to use in other types of reciprocating pumps, such as reciprocating pumps used in mining operations, and the like.

The market demand for 7500 psi land drilling has continued to increase and forecasted to remain strong as drillers and operators seek to complete wells more faster and more efficiently. Premium has the expertise and ability to convert existing 5000 psi pump systems with our 7500 psi fluid end upgrade. In addition to replacing the existing valve-over-valve module with our proven L-Shaped design, a typical conversion also includes an upgraded liner retainer system, discharge cross/ strainer, high-pressure discharge manifold and 7500 psi pulsation dampener.

BOMCO/Emsco Mud Pumps:F2200HL, F1600HL, F-1300, F-1600, FB1300, FB1600, F-800, F-1000, F-500, F-350, DB-550, DA-700, FA-1600/1300, FC-2200, D-300/500, D-375, D-700,