WO2015065755A1 - Outil de vibration - Google Patents

Outil de vibration Download PDF

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Publication number
WO2015065755A1
WO2015065755A1 PCT/US2014/061475 US2014061475W WO2015065755A1 WO 2015065755 A1 WO2015065755 A1 WO 2015065755A1 US 2014061475 W US2014061475 W US 2014061475W WO 2015065755 A1 WO2015065755 A1 WO 2015065755A1
Authority
WO
WIPO (PCT)
Prior art keywords
subassembly
valve
piston
valve mechanism
vibration tool
Prior art date
Application number
PCT/US2014/061475
Other languages
English (en)
Inventor
Baozhong Yang
Tommy G. Ray
Jianbing Hu
Zhenbi Su
Dwayne P. Terracina
Xin Hu
Original Assignee
Schlumberger Canada Limited
Services Petroliers Schlumberger
Schlumberger Holdings Limited
Schlumberger Technology B.V.
Smith International, Inc.
Prad Research And Development Limited
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schlumberger Canada Limited, Services Petroliers Schlumberger, Schlumberger Holdings Limited, Schlumberger Technology B.V., Smith International, Inc., Prad Research And Development Limited filed Critical Schlumberger Canada Limited
Publication of WO2015065755A1 publication Critical patent/WO2015065755A1/fr

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B7/00—Special methods or apparatus for drilling
    • E21B7/24—Drilling using vibrating or oscillating means, e.g. out-of-balance masses
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B28/00—Vibration generating arrangements for boreholes or wells, e.g. for stimulating production

Definitions

  • aspects of the disclosure relate to drilling of geological stratum. More
  • aspects of the disclosure relate to a vibration tool and methods of use of the vibration tool.
  • a drill bit may be carried on an end portion of a drill pipe.
  • deviated or extended reach wells may be drilled to facilitate the recovery of hydrocarbons.
  • extended reach wells may be used to increase a recovery rate of hydrocarbons while limiting operational costs.
  • a friction of a drill string against a wellbore may be generated.
  • horizontal sections of the wellbore may produce higher friction than vertical or directional sections of the wellbore. If a frictional force reaches a certain level, then the drill string may go into compression and ultimately buckle. Once buckling occurs, then the drill string may not be able to advance farther in the wellbore.
  • Such a stage may be referred to as drill string lockup.
  • the amount of drill string lockup may limit a depth at which a drilling tool or fluid can be delivered into the wellbore, thereby limiting a reach of the well drilling operations.
  • the vibration tool may include a housing having a bore extending therethrough.
  • the vibration tool may also include a piston subassembly positioned inside the bore, where the piston subassembly is arranged to oscillate when fluid flow inside the piston subassembly exceeds a predetermined flow rate.
  • the vibration tool may further include a valve mechanism positioned at least partially around the piston subassembly, where the valve mechanism is arranged to restrict fluid to flow inside the piston subassembly when the valve mechanism is in a closed state and to allow the fluid to flow from the piston subassembly to the bore when the valve mechanism is in an open state.
  • a latching valve subassembly for use in a tool may include a valve sleeve movably disposed at least partially over a cylindrical body, where the valve sleeve includes one or more communication ports that are aligned with one or more ports of the cylindrical body when the valve sleeve is in a first state.
  • the latching valve subassembly may also include one or more latching mechanisms coupled to the valve sleeve. The latching mechanisms may protrude from an inner diameter of the valve sleeve.
  • an impact mitigation subassembly for use in a tool may include an impact cap arranged to couple to an end portion of a moving body.
  • the impact mitigation subassembly may also include one or more springs disposed on an inside base of the impact cap, where the springs are arranged to allow displacement of the moving body within the impact cap when movement of the impact cap is arrested.
  • Figure 1 illustrates a cross-sectional view of a vibration tool in accordance with implementations of various techniques disclosed herein.
  • Figures 2 and 3 illustrate a cross-sectional view of the vibration tool in a "start" position in accordance with implementations of various techniques disclosed herein.
  • FIG. 4-15 illustrate a cross-sectional view of the vibration tool in accordance with implementations of various techniques disclosed herein.
  • Figures 16 and 17 illustrate a cross-sectional view of the vibration tool in the "start" position in accordance with implementations of various techniques disclosed herein.
  • Figure 18 illustrates a cross-sectional view of a vibration tool in accordance with implementations of various techniques disclosed herein.
  • Figure 19 illustrates a side view of a sleeve of the latching valve subassembly in accordance with implementations of various techniques disclosed herein.
  • Figure 20 illustrates a top view of latching mechanisms of the latching valve subassembly in accordance with implementations of various techniques disclosed herein.
  • Figures 21 and 22 illustrate a cross-sectional view of the latching valve subassembly in accordance with implementations of various techniques disclosed herein.
  • Figure 23 illustrates a cross-sectional view of the vibration tool in a "start" position in accordance with implementations of various techniques disclosed herein.
  • FIG. 24-28 illustrate a cross-sectional view of the vibration tool in accordance with implementations of various techniques disclosed herein.
  • Figure 29 illustrates a cross-sectional view of the vibration tool in the "start" position in accordance with implementations of various techniques disclosed herein.
  • Figure 30 illustrates a cross-sectional view of an impact mitigation subassembly in accordance with implementations of various techniques disclosed herein.
  • Figure 31 illustrates a side view of the moving body in accordance with implementations of various techniques disclosed herein.
  • Figure 32 illustrates a side view of an impact mitigation subassembly in accordance with implementations of various techniques disclosed herein.
  • first, second, etc. may be used herein to describe various elements, these elements should not be limited by these terms. These terms are used to distinguish one element from another. For example, a first object could be termed a second object, and, similarly, a second object could be termed a first object, without departing from the scope of the claims.
  • the first object and the second object are both objects, respectively, but they are not to be considered the same object.
  • the terms “up” and “down”; “upper” and “lower”; “upwardly” and downwardly”; “below” and “above”; and other similar terms indicating relative positions above or below a given point or element may be used in connection with some implementations of various technologies described herein. However, when applied to equipment and methods for use in wells or boreholes that are deviated or horizontal, or when applied to equipment and methods that when arranged in a well or borehole are in a deviated or horizontal orientation, such terms may refer to a left to right, right to left, or other relationships as appropriate.
  • Figure 1 illustrates a cross-sectional view of a vibration tool 100 in accordance with implementations of various techniques described herein.
  • One or more components of the vibration tool 100 may be composed of steel, tungsten carbide, or any other implementation known to those skilled in the art.
  • the vibration tool 100 may include a housing 102 having an upper sub 104, a central sub 106, and a lower sub 108.
  • the upper sub 104 may be coupled to the central sub 106, and the central sub 106 may be coupled to the lower sub 108 through the use of threads, bolts, welds, or any other attachment feature known to those skilled in the art.
  • the housing 102 may be oriented such that the upper sub 104 may engage with uphole members of a drill string (not shown), and the lower sub 108 may engage with downhole members of the drill string.
  • the vibration tool 100 may also include a piston subassembly 1 10 disposed within a housing bore 103 of the housing 102.
  • the piston subassembly 1 10 may include a piston 1 12 having a piston bore 1 14, where an uphole end portion of the piston bore 1 14 may receive a fluid flow from a bore of the upper sub 104.
  • a downhole end portion of the piston bore 1 14 may be arranged as a nozzle 1 16, where the nozzle 1 16 may allow fluid to exit from the piston bore 1 14.
  • the piston 1 12 may also include one or more bypass ports 1 18 disposed proximate to the downhole end portion of the piston bore 1 14, where the bypass ports may provide one or more channels for the fluid to flow from the piston bore 1 14 to the housing bore 103, as described in more detail below.
  • the piston subassembly 1 10 may also include a valve stopper 120, which may be coupled to and/or disposed around the piston 1 12.
  • the valve stopper 120 may be coupled to the piston 1 12 through the use of threads, bolts, welds, or any other attachment feature known to those skilled in the art.
  • the valve stopper 120 may be configured to slide onto an outer diameter of the piston 1 12, beginning at a downhole end portion of the piston 1 12, until an uphole end portion of the valve stopper 120 abuts a shoulder along the outer diameter of the piston 1 12.
  • the piston subassembly 1 10 may further include a lower impact cap 122, which may be coupled to and/or disposed around the piston 1 12.
  • the lower impact cap 122 may be coupled to the piston 1 12 through the use of threads, bolts, welds, or any other attachment feature known to those skilled in the art.
  • the piston subassembly 1 10 may be oriented such that the valve stopper 120 is positioned uphole relative to the lower impact cap 122. In particular, once coupled to the piston 1 12, the lower impact cap 122 may abut against the valve stopper 120 so that movement of the valve stopper 120 relative to the piston 1 12 may be arrested.
  • the piston 1 12, the valve stopper 120, and/or the lower impact cap 122 may be configured to move in conjunction with one another.
  • the lower impact cap 122 may be coupled to a downhole end portion of the piston subassembly 1 10.
  • the piston subassembly 1 10 may be configured so that fluid may flow from the nozzle 1 16 to a bore of the lower impact cap 122, and then flow from the bore of the lower impact cap 122 to the bore of the lower sub 108.
  • the lower impact cap 122 may function as a weight whose impact with the housing 102 may create vibrations throughout a drilling tool, as described in more detail below.
  • the vibration tool 100 may also include a retainer cap 124 within the housing bore 103, where the retainer cap 124 may be coupled to an inner diameter of the housing 102 through the use of threads, bolts, welds, or any other attachment feature known to those skilled in the art.
  • the retainer cap 124 may be coupled to an inner diameter of the upper sub 104.
  • the retainer cap 124 may be threaded in an uphole direction 101 until its uphole end portion abuts a shoulder of the inner diameter of the upper sub 104.
  • the retainer cap 124 may also be disposed around the piston 1 12, such that the piston 1 12 may be allowed to move in a longitudinal direction within the retainer cap 124.
  • the retainer cap 124 may include one or more static seals and/or dynamic seals to prevent fluid flow from passing axially through the housing bore 103.
  • the vibration tool 100 may also include a puller cover 126 within the housing bore 103, where the puller cover 126 may be disposed around the piston 1 12.
  • the puller cover 126 may include a head section 127 having a greater outer diameter than the rest of the puller cover 126.
  • the head section 127 may be oriented such that its uphole end portion may abut a downhole end portion of the retainer cap 124.
  • at least a portion of the downhole end portion of the head section 127 may be seated against a shoulder formed by an uphole end portion of the central sub 106.
  • the retainer cap 124 and the puller cover 126 may be coupled or affixed such that neither component may move with respect to the housing 102.
  • the puller cover 126 may be coupled or affixed such that the retainer cap 124 and the puller cover 126 may be prevented from rotating.
  • the vibration tool 100 may also include an upper spring 130 extending in the uphole direction 101 from the retainer cap 124.
  • the upper spring 130 may also be coupled to the piston 1 12.
  • the upper spring 130 may be a coiled spring, a Belleville washer spring, or any other biasing mechanism known to those skilled in the art.
  • the piston 1 12 may include a head section 132 having a greater outer diameter than the rest of the piston 1 12.
  • the upper spring 130 may be coupled to a downhole end portion of the head section 132.
  • the upper spring 130 may bias the piston subassembly 1 10 in the uphole direction 101 such that the vibration tool 100 is in a "start" position. In this position, the piston subassembly 1 10, and the piston 1 12 in particular, may be seated against an upper shoulder 134, which may be located within the bore of the upper sub 104. In particular, when the piston subassembly 1 10 is in the "start" position, an uphole side of the head section 132 may be seated against the upper shoulder 134.
  • a preload bias may be applied to the upper spring 130 when a retainer cap 124 is coupled to the housing 102. As an example, the preload bias may be about 600 pound force (Ibf).
  • the vibration tool 100 may also include a moving valve mechanism 140, where the moving valve mechanism 140 may be movably disposed around the piston 1 12.
  • the moving valve mechanism 140 may be a sleeve which may be moved in a longitudinal direction with respect to the piston 1 12.
  • a valve spring 142 may be coupled to an uphole end portion of the moving valve mechanism 140 and to a downhole end portion of the puller cover 127.
  • the valve spring 142 may be a coiled spring, a Belleville washer spring, or any other biasing mechanism known to those skilled in the art.
  • the valve spring 142 When the vibration tool 100 is in its "start" position, the valve spring 142 may bias the moving valve mechanism 140 in a downhole direction 105.
  • valve spring 142 may bias the moving valve mechanism 140 into contact with the valve stopper 120, such that a face seal may be created where the downhole end portion 145 of the moving valve mechanism 140 meets the uphole end portion 146 of the valve stopper 120.
  • a metal-to-metal face seal may be formed where the moving valve mechanism 140 meets the valve stopper 120.
  • a rubber-to-rubber face seal or a rubber-to-metal seal may be formed where the moving valve mechanism 140 meets the valve stopper 120.
  • the bypass ports 1 18 of the piston 1 12 may be covered, causing fluid from the piston bore 1 14 to flow primarily through the nozzle 1 16, rather than into the housing bore 103 via the bypass ports 1 18.
  • the moving valve mechanism 140 may be said to be in its "closed” state.
  • the valve spring 142 may be in compression when the vibration tool 100 is in its "start” position. In this position, the valve spring 142 may apply about 80- 100 Ibf to the moving valve mechanism 140.
  • the moving valve mechanism 140 may be positioned such that it may not cover the bypass ports 1 18, allowing fluid to flow into the housing bore 103 from the piston bore 1 14. In such an implementation, the moving valve mechanism 140 may be said to be in its "open” state, as described in more detail below.
  • One or more static seals and one or more dynamic seals may be disposed within the moving valve mechanism 140.
  • the moving valve mechanism 140 may also include a lower head section 147 and an upper head section 148, where the head sections may have a greater outer diameter than the rest of the moving valve mechanism 140.
  • the moving valve mechanism 140 may be oriented so that the lower head section 147 may be positioned downhole with respect to the upper head section 148.
  • an uphole end portion of the lower head section 147 may be seated against one or more pins 150 protruding from the inner diameter of the housing 102.
  • the pins 150 may have a flat face which may interact with the head sections of the moving valve mechanism 140, as described in more detail below.
  • the vibration tool 100 may use four pins protruding from an inner diameter of the central sub 106.
  • the vibration tool 100 may also include a bottom impact surface 160 and/or a top impact surface 164.
  • the bottom impact surface 160 may be coupled to a lower shoulder of the housing 102.
  • the bottom impact surface 160 may be coupled to a lower shoulder 162 of the lower sub 108.
  • the top impact surface 164 may be coupled to an upper shoulder of the housing 102, such as an upper shoulder 134 of the top sub 104.
  • the bottom impact surface 160 and/or the top impact surface 164 may be designed to receive an impact from a moving body, such as the piston subassembly 1 10, while limiting damage to the housing 102.
  • the lower shoulder 162 and/or the upper shoulder 134 may be designed to receive an impact from the moving body without the use of the impact surfaces.
  • the bottom impact surface 160 and/or the top impact surface 164 may be composed of a less expensive material than other components of the vibration tool 100.
  • the lower impact cap 122 when the vibration tool 100 is at its "start" position, the lower impact cap 122 may be positioned at a specified distance away from the bottom impact surface 160.
  • Figures 2 and 3 illustrate a cross-sectional view of the vibration tool 100 in a "start” position in accordance with implementations of various techniques described herein.
  • Figure 3, in particular, illustrates a close-up view of the vibration tool 100.
  • the upper spring 130 may bias the piston subassembly 1 10 into its "start” position, i.e., into contact with the upper shoulder 134 and/or the top impact surface 164.
  • the upper spring 130 may be in compression when biasing the piston subassembly 1 10. Additionally, the valve spring 142 may bias the moving valve mechanism 140 into contact with the valve stopper 1 20, such that a face seal may be formed and the moving valve mechanism 140 may be in its "closed" state.
  • a fluid flow may pass from the bore of the upper sub 104 and through the piston bore 1 14, the nozzle 1 16, the bore of the lower impact cap 122, and the bore of the lower sub 108.
  • the fluid flow may have a flow rate less than a predetermined threshold flow rate.
  • the fluid flow may include a flow of drilling fluid, drilling mud, or any other implementation known to those skilled in the art.
  • the vibration tool 100 With the flow rate less than the predetermined threshold flow rate, the vibration tool 100 remains at its "start” position. In this position, the moving valve mechanism 140 may remain in its "closed” state with the face seal intact, allowing fluid to flow through to the bore of the lower sub 108 via the nozzle 1 16. Further, at the "start” position, the fluid flow may be forced to exit the piston bore 1 14 solely through the nozzle 1 16, causing fluid pressure to build within the vibration tool 100.
  • the fluid flow rate may reach an amount that is greater than or equal to the predetermined threshold flow rate.
  • a fluid pressure differential across the piston subassembly 1 10 may increase. Specifically, a fluid pressure may increase across the piston 1 12, and within the piston bore 1 14 in particular, which may lead to an increase in a pressure force acting on an uphole end portion of the piston 1 12. As a result of this pressure force, a force of the upper spring 130 may be overcome, thereby causing the piston subassembly 1 10 to move in a downhole direction 105.
  • the predetermined threshold flow rate may be defined as a flow rate needed to move the piston subassembly 1 10 in the downhole direction 105. In another implementation, the predetermined threshold flow rate may be at least partly based on the static seals and/or the dynamic seals disposed in the retainer cap 124.
  • Figures 4 and 5 illustrate a cross-sectional view of the vibration tool 100 in accordance with implementations of various techniques described herein.
  • Figure 5, in particular, illustrates a close-up view of the vibration tool 100.
  • the piston subassembly 1 10 may move away from the "start" position in a downhole direction 105 due to a momentum of the fluid flow and the pressure force acting on the piston subassembly 1 10, overcoming the upper spring 130.
  • the upper spring 130 may remain in compression with the piston 1 12.
  • the piston 1 12, the valve stopper 120, and/or the lower impact cap 122 may move in the downhole direction 105 together.
  • a momentum of the lower impact cap 122 may also help to move the piston subassembly 1 10 in the downhole direction 105.
  • the moving valve mechanism 140 may move with the piston subassembly
  • the pressure force may act on a downhole portion of the moving valve mechanism 140, proximate to where the moving valve mechanism 140 abuts against the valve stopper 120.
  • the pressure force acting on this downhole portion may cause the moving valve mechanism 140 to maintain its face seal and move in the downhole direction 105 with the valve stopper 120.
  • this pressure force may be greater than a force of the valve spring 142.
  • the valve spring 142 may move into tension with the moving valve mechanism 140.
  • the moving valve mechanism 140 may maintain its face seal with the valve stopper 120, moving in conjunction with the piston subassembly 1 10.
  • the pressure force may be about 500 to about 1 ,500 Ibf, and the force of the valve spring 142 may be about 100 Ibf.
  • the moving valve mechanism 140 As the moving valve mechanism 140 travels in the downhole direction 105, its lower head section 147 may no longer abut the pins 150.
  • the moving valve mechanism 140 may move a sufficient distance such that a downhole end portion of its upper head section 148 may come into contact with the pins 150, as shown in Figures 4 and 5.
  • further downhole movement of the moving valve mechanism 140 may be arrested.
  • the piston subassembly 1 10 may still be positioned at a distance apart from the bottom impact surface 160 and/or the lower shoulder 162 when the pins 150 come into contact with the upper head section 148.
  • Figures 6 and 7 illustrate a cross-sectional view of the vibration tool 100 in accordance with implementations of various techniques described herein.
  • Figure 7, in particular, illustrates a close-up view of the vibration tool 100.
  • further downhole movement of the moving valve mechanism 140 may be arrested by the pins 150.
  • the pressure force acting on the piston subassembly 1 10 may continue to move the piston subassembly 1 10 in the downhole direction 105.
  • the piston subassembly 1 10 may separate from the moving valve mechanism 140, breaking the face seal where the downhole end portion 145 of the moving valve mechanism 140 meets the uphole end portion 146 of the valve stopper 120. Once the face seal has opened, the moving valve mechanism 140 may be said to be in its "open" state.
  • the piston subassembly 1 10 may move in the downhole direction 105 until impacting the bottom impact surface 160 and/or the lower shoulder 162, where a downhole end portion of the lower impact cap 122 may be seated against the bottom impact surface 160 and/or the lower shoulder 162.
  • vibrations may be created throughout the housing 102, which may be imparted to the vibration tool 100 and to a drill string (not shown).
  • the fluid flow may travel from the piston bore 1 14 and through the bypass ports 1 18, reaching the housing bore 103.
  • the fluid pressure across the piston subassembly 1 10 may then decrease.
  • the fluid pressure may decrease from about 500 pounds per square inch (psi) to about 40 psi.
  • the initial separation between the moving valve mechanism 140 and the valve stopper 120, which causes the fluid pressure to decrease may be about 0.1 inches.
  • Figures 8 and 9 illustrate a cross-sectional view of the vibration tool 100 in accordance with implementations of various techniques described herein.
  • Figure 9, in particular, illustrates a close-up view of the vibration tool 100.
  • the force of the valve spring 142 may overcome this pressure force acting on the moving valve mechanism 140, thereby biasing the moving valve mechanism 140 in the uphole direction 101 .
  • the moving valve mechanism 140 may move in the uphole direction 101 while the lower impact cap 122 of the piston subassembly 1 10 largely maintains its position against the bottom impact surface 160 and/or the lower shoulder 162.
  • valve spring 142 biases the moving valve mechanism 140 in the uphole direction 101 , the downhole end portion of the upper head section 148 may separate from the pins 150.
  • valve spring 142 may bias the moving valve mechanism 140 such that the moving valve mechanism 140 is "fully open,” i.e., at a maximum distance from the valve stopper 120. When the moving valve mechanism 140 is at such a distance, the fluid may flow through the bypass ports 1 18 with the least obstruction.
  • the valve spring 142 may bias the moving valve mechanism 140 in the uphole direction 101 until its lower head section 147 comes into contact with a port shoulder 170 of the piston 1 12.
  • a downhole shoulder 172 of the lower head section 147 may be seated against the port shoulder 170, which may be located proximate to the bypass ports 1 18.
  • movement of the moving valve mechanism 140 may be arrested until the piston subassembly 1 10 begins to move.
  • the valve spring 142 may continue to bias the moving valve mechanism 140 in the uphole direction 101 , but the uphole movement of the moving valve mechanism 140 may be restricted by the port shoulder 170.
  • the moving valve mechanism 140 may move in the uphole direction 101 as far as may be allowed by the positioning of the piston subassembly 1 10.
  • uphole movement of the piston subassembly 1 10 may be slower than that of the moving valve mechanism 140.
  • Figures 10 and 1 1 illustrate a cross-sectional view of the vibration tool 100 in accordance with implementations of various techniques described herein.
  • Figure 1 1 illustrates a close-up view of the vibration tool 100.
  • the upper spring 130 may overcome the pressure force acting on the uphole end portion of the piston 1 12 and move the piston subassembly 1 10 in the uphole direction 101 .
  • the lower impact cap 122 may no longer be seated against the bottom impact surface 160 and/or the lower shoulder 162.
  • the moving valve mechanism 140 may remain seated against the port shoulder 170 as the moving valve mechanism 140 travels in the uphole direction 101 .
  • valve spring 142 may eventually reach a neutral state as the moving valve mechanism 140 travels in the uphole direction 101 .
  • the valve spring 142 may be neither compressed nor in tension, and the moving valve mechanism 140 may not be biased in any direction.
  • the piston subassembly 1 10 may continue to travel in the uphole direction 101 .
  • Figures 12 and 13 illustrate a cross-sectional view of the vibration tool 100 in accordance with implementations of various techniques described herein.
  • Figure 13, in particular, illustrates a close-up view of the vibration tool 100.
  • the upper spring 130 may continue to bias the piston subassembly 1 10 in the uphole direction 101 .
  • the distance between the valve stopper 120 and the moving valve mechanism 140 may begin to decrease.
  • pressure from the fluid flowing through the bypass ports 1 18 may begin to exert a force on the downhole end portion of the moving valve mechanism 140.
  • the force may begin to bias the moving valve mechanism 140 in the downhole direction 105.
  • the moving valve mechanism 140 may compress the valve spring 142, causing the valve spring 142 to exert a force in the downhole direction 105 towards the valve stopper 120.
  • Figures 14 and 15 illustrate a cross-sectional view of the vibration tool 100 in accordance with implementations of various techniques described herein.
  • Figure 15, in particular, illustrates a close-up view of the vibration tool 100.
  • the upper spring 130 may continue to bias the piston subassembly 1 10 in the uphole direction 101 .
  • the pressure force of the fluid flowing through the bypass ports 1 18 may continue to bias the moving valve mechanism 140 in the downhole direction 105, while the valve spring 142 may continue to exert a bias on the moving valve mechanism 140 in the downhole direction 105.
  • valve spring 142 may bias the moving valve mechanism 140 into contact with the valve stopper 120, such that the face seal may be formed and the moving valve mechanism 140 may be in its "closed" state, as shown in Figures 16 and 17.
  • the lower head section 147 of the moving valve mechanism 140 may come into contact with the pins 150 before the face seal may be re-created.
  • the face seal may be re-created before the lower head section 147 may come into contact with the pins 150.
  • Figures 16 and 17 illustrate a cross-sectional view of the vibration tool 100 in the "start” position in accordance with implementations of various techniques described herein.
  • Figure 17, in particular, illustrates a close-up view of the vibration tool 100.
  • the upper spring 130 may bias the piston subassembly 1 10 back to its "start" position, i.e., into contact with the upper shoulder 134 and/or the top impact surface 164.
  • vibrations may be created throughout the housing 102, which may be imparted to the vibration tool 100 and to a drill string (not shown).
  • the moving valve mechanism 140 may be in its "closed” state.
  • the fluid flow may again pass from the bore of the upper sub 104 and through the piston bore 1 14, the nozzle 1 16, the bore of the lower impact cap 122, and the bore of the lower sub 108. If the fluid flow rate remains greater than or equal to the predetermined threshold flow rate, then the fluid pressure may again increase across the piston 1 12, leading to an increase in the pressure force acting on the uphole end portion of the piston 1 12. The vibration tool may then again operate as described with respect to Figures 2-17.
  • the vibration tool 100 may cause the piston subassembly 1 10 to oscillate in the uphole direction 101 and the downhole direction 105, causing repeated impacts against the housing 102 and/or the impact surfaces. As a result, the vibration tool 100 may produce vibrations which may be imparted to the drill string (not shown). In one implementation, the vibration tool 100 may perform one cycle as described with respect to Figures 2-17 at a rate of about ten times per second.
  • Figure 18 illustrates a cross-sectional view of a vibration tool 200 in accordance with implementations of various techniques described herein.
  • One or more components of the vibration tool 200 may be composed of steel, tungsten carbide, or any other implementation known to those skilled in the art.
  • the vibration tool 200 may include a housing 202 having a housing bore 203 and composed of an upper sub 204 and a lower sub 208.
  • the upper sub 204 may be coupled to the lower sub 208 through the use of threads, bolts, welds, or any other attachment feature known to those skilled in the art.
  • the housing 202 may be oriented such that the upper sub 204 may engage with uphole members of a drill string (not shown), and the lower sub 208 may engage with downhole members of the drill string.
  • the vibration tool 200 may include a piston subassembly 210 composed of a piston 212 having a piston bore 214, a nozzle 216, and one or more bypass ports 218.
  • the piston subassembly 210 may further include a lower impact cap 222, where the lower impact cap 222 may be coupled to and/or disposed around the piston 212.
  • the piston subassembly 210 may be similar to the piston subassembly 1 10.
  • the vibration tool 200 may also include a retainer cap 224, which may be coupled to an inner diameter of the housing 202 through the use of threads, bolts, welds, or any other attachment feature known to those skilled in the art.
  • the retainer cap 224 may also include an upper spring 230 extending in the uphole direction 201 from the retainer cap 224.
  • the upper spring 230 may also be coupled to the piston 212.
  • the retainer cap 224 and the upper spring 230 may be similar to the retainer cap 124 and the upper spring 130, respectively.
  • the vibration tool 200 may also include a latching valve subassembly 240, which may be movably disposed around the piston 212.
  • the latching valve subassembly 240 may be coupled to a valve spring 242, which may be coupled to an uphole end portion of the lower impact cap 222 and to a downhole end portion of the latching valve subassembly 240.
  • the latching valve subassembly 240 may include a sleeve 243 which may be moveable in a longitudinal direction with respect to the piston 212.
  • One or more latching mechanisms 245 ( Figures 20 to 22) may be attached or coupled to the sleeve 243, where the latching mechanisms 245 may be configured to couple to the piston 212.
  • the latching valve subassembly 240 may include one or more static seals and/or dynamic seals attached to the sleeve 243, where the seals may be configured inhibit a fluid flow between the piston 212 and the housing bore 203 and/or centralize the latching valve subassembly 240.
  • the latching mechanisms 245 may engage with one or more first latch stops 280 on an outer diameter of the piston 212, such that the sleeve 243 may cover the bypass ports 218.
  • first latch stops 280 on an outer diameter of the piston 212
  • the sleeve 243 covers the bypass ports 218, fluid from the piston bore 214 may flow primarily through the nozzle 216 rather than into the housing bore 203 via the bypass ports 218.
  • the latching valve subassembly 240 may be said to be in its "closed” state.
  • the latching mechanisms 245 may also engage with one or more second latch stops 282 on the outer diameter of the piston 212, such that the bypass ports 218 may be uncovered, allowing fluid to flow into the housing bore 203 from the piston bore 214.
  • the latching valve subassembly 240 may be said to be in its "open” state.
  • the latching valve subassembly is described in more detail with respect to Figures 19-22.
  • Figure 19 illustrates a side view of the sleeve 243 of the latching valve subassembly 240 in accordance with implementations of various techniques described herein.
  • the sleeve 243 may be cylindrical in shape and configured to move in a longitudinal direction along an outer diameter of the piston 212.
  • the sleeve 243 may include one or more latch holes 244 configured to engage with one or more latching mechanisms 245 shown in Figure 20.
  • FIG 20 illustrates a top view of the latching mechanisms 245 of the latching valve subassembly 240 in accordance with implementations of various techniques described herein.
  • the latching mechanisms 245 may each include a bar 290 attached to a raised pocket 291 , inside of which may include a ball 292.
  • the ball 292 may be designed to roll and/or be displaced inside of the pocket 291 .
  • each pocket 291 When coupled to the sleeve 243, each pocket 291 may be disposed through the latch hole 244, such that the ball 292 may protrude from the inner diameter of the sleeve 243.
  • the bar 290 may be attached to the sleeve 243 via screws or any other fastening means known to those skilled in the art.
  • the sleeve 243 may also include one or more balance ports for balancing pressure across the latching mechanisms 245.
  • the sleeve 243 may also include one or more communication ports 246, which may allow the fluid flow to pass to the housing bore 203.
  • the communication ports 246 may align with the bypass ports 218 to allow fluid to flow into the housing bore 203 from the piston bore 214.
  • the communication ports 246 and the bypass ports 21 8 may be misaligned, thereby creating a seal between the piston 212 and the sleeve 243 and blocking the fluid flow from passing through the bypass ports 218.
  • the piston 212 may include bypass ports 218 circumferentially positioned at a plurality of longitudinal positions, while the sleeve 243 may also include communication ports 246 circumferentially positioned at a plurality of longitudinal positions.
  • the number of communication ports 246 may be equal to the number of bypass ports 218. In another implementation, the number of communication ports 246 may be different than the number of bypass ports 218.
  • the piston 212 may include four bypass ports 218 circumferentially spaced at each longitudinal position, while the sleeve 243 may include five communication ports 246 circumferentially spaced at each longitudinal position. In such an implementation, when the latching valve subassembly 240 is in the "open" state, the differing number of communication ports 246 and bypass ports 218 may align to create a sufficient opening area for the fluid flow to pass to the housing bore 203, regardless of a relative angular position of the sleeve 243 to the piston 212.
  • Figures 21 and 22 illustrate a cross-sectional view of the latching valve subassembly 240 in accordance with implementations of various techniques described herein.
  • the sleeve 243 may be disposed around the piston 212, where latching mechanisms 245 of the sleeve 243 may engage an outer diameter of the piston 212.
  • the ball 292 may protrude from the inner diameter of the sleeve 243 and interact with the piston 212.
  • Figure 21 illustrates the latching valve subassembly 240 in its "closed” state.
  • the bypass ports 218 and the communication ports 246 may be misaligned.
  • the latching mechanisms 245, e.g., the ball 292 may engage with the first latch stops 280 of the outer diameter of the piston 212.
  • the first latch stops 280 may be indentations of a specified distance in the outer diameter of the piston 212.
  • the latching valve subassembly 240 While engaged with the first latch stops 280, the latching valve subassembly 240 may be allowed to move in a longitudinal direction for the specified distance.
  • a first latch stop 280 may be positioned downhole from a second latch stop 282.
  • An uphole end portion of the first latch stop 280 may be bounded by a bumper 281 , and a downhole end portion of the first latch stop 280 may be bounded by the outer diameter of the piston 212.
  • the bumper 281 may be a portion of the piston 212 having an outer diameter that is less than the rest of the piston 212.
  • the bumper 281 may be configured to allow the ball 292 to traverse the piston 212 and into the second latch stop 282, as described below.
  • Figure 22 illustrates the latching valve subassembly 240 in its "open” state.
  • the bypass ports 218 and the communication ports 246 may be aligned with one another.
  • the latching mechanisms 245, e.g., the ball 292 may engage with the second latch stops 282 of the outer diameter of the piston 212.
  • the second latch stops 282 may be similar to the first latch stops 280.
  • a downhole end portion of the second latch stop 282 may be bounded by the bumper 281 , and an uphole end portion of the second latch stop 282 may be bounded by the outer diameter of the piston 212.
  • a minimum force may be applied to the latching valve subassembly 240.
  • the predetermined force may move the latching valve subassembly 240 between the "closed” and “open” positions.
  • the minimum force used to overcome the bumper 281 may be based on a size of the latching mechanisms 245.
  • the upper spring 230 may bias the piston subassembly 210 in the uphole direction 201 such that the vibration tool 200 is in a "start" position. In such a "start” position, the piston subassembly 210, and the piston 212 in particular, may be seated against an upper shoulder 234 of the upper sub 204.
  • the latching valve subassembly 240 may have its uphole end portion seated against a downhole end portion of the retainer cap 224.
  • the valve spring 242 may help to bias the latching valve subassembly 240 against the retainer cap 224.
  • the latching valve subassembly 240 may be in its "closed” state.
  • the vibration tool 200 may also include a bottom impact surface 260 and/or a top impact surface 264.
  • the lower impact cap 222 may be positioned at a specified distance away from the bottom impact surface 260.
  • Figure 23 illustrates a cross-sectional view of the vibration tool 200 in a "start" position in accordance with implementations of various techniques described herein.
  • the upper spring 230 may bias the piston subassembly 210 into its "start” position, i.e., into contact with the upper shoulder 234.
  • the upper spring 230 may be in compression when biasing the piston subassembly 210.
  • a top impact surface 264 may be coupled to the upper shoulder 234.
  • a fluid flow may pass from the bore of the upper sub 204 and through the piston bore 214, the nozzle 216, the bore of the lower impact cap 222, and the bore of the lower sub 208.
  • the fluid flow may have a flow rate less than a predetermined threshold flow rate. With the flow rate less than the predetermined threshold flow rate, the vibration tool 200 remains at its "start” position. In its “start” position, the latching valve subassembly 240 may remain in its “closed” state with the seal between the piston 212 and the sleeve 243 intact, allowing fluid to flow through to the bore of the lower sub 208 via the nozzle 216.
  • the fluid flow rate may reach an amount that is greater than or equal to the predetermined threshold flow rate.
  • the vibration tool 200 is in its "start” position and the latching valve subassembly 240 is in its "closed” state, the fluid flow may be forced to exit the piston bore 214 solely through the nozzle 216, causing fluid pressure to build within the vibration tool 200. Similar to vibration tool 100, an increase in a pressure force may act on an uphole end portion of the piston 212, overcoming a force of the upper spring 230, and causing the piston subassembly 210 to move in a downhole direction 205.
  • Figure 24 illustrates a cross-sectional view of the vibration tool 200 in accordance with implementations of various techniques described herein.
  • the piston subassembly 210 may move away from the "start" position in a downhole direction 205 due to a momentum of the fluid flow and the pressure force acting on the uphole end portion of the piston 212.
  • the latching valve subassembly 240 may move with the piston subassembly 210.
  • a portion of its sleeve 243 may come into contact with one or more pins 250.
  • the pins 250 may be similar to the pins 150. Upon coming into contact with the pins 250, further downhole movement of the latching valve subassembly 240 may be arrested.
  • the piston subassembly 210 may still be positioned at a distance apart from the bottom impact surface 260 and/or the lower shoulder 262.
  • the pins 250 may be disposed inside a pathway located in the sleeve 243, where the pins 250 may travel along the pathway as the latching valve subassembly 240 moves in the uphole direction 201 or the downhole direction 205.
  • Figure 25 illustrates a cross-sectional view of the vibration tool 200 in accordance with implementations of various techniques described herein.
  • further downhole movement of the latching valve subassembly 240 may be arrested by the pins 250.
  • the pressure force acting on the piston subassembly 210 may continue to move the piston subassembly 210 in the downhole direction 205.
  • the arrested latching valve subassembly 240 may begin to move from its "closed” state to its "open” state.
  • the balls 292 may be forced to travel from the first latch stops 280 to the second latch stops 282.
  • the piston subassembly 210 may move in the downhole direction 205 until impacting the bottom impact surface 260 and/or the lower shoulder 262, where a downhole end portion of the lower impact cap 222 may be seated against the bottom impact surface 260 and/or the lower shoulder 262.
  • vibrations may be created throughout the housing 202, which may be imparted to the vibration tool 200 and to a drill string (not shown).
  • FIG. 26 illustrates a cross-sectional view of the vibration tool 200 in accordance with implementations of various techniques described herein.
  • the latching valve subassembly 240 may be in its "open" state.
  • the balls 292 may have traversed in the uphole direction 201 along the piston 212, traveling from the first latch stops 280 to the second latch stops 282.
  • a bias of the valve spring 242, acting on the latching valve subassembly 240 may help to move the balls 292 to the second latch stops 282 in the uphole direction 201 .
  • FIG. 27 illustrates a cross-sectional view of the vibration tool 200 in accordance with implementations of various techniques described herein.
  • the upper spring 230 may overcome the pressure force acting on the uphole end portion of the piston 212 and move the piston subassembly 210 in the uphole direction 201 .
  • the lower impact cap 222 may no longer be seated against the bottom impact surface 260 and/or the lower shoulder 262.
  • the latching valve subassembly 240 may travel in the uphole direction 201 in conjunction with the piston subassembly 210 while remaining in its "open" state.
  • the latching valve subassembly 240 may eventually have its uphole end portion again seated against a downhole end portion of the retainer cap 224.
  • the valve spring 242 may again help to bias the latching valve subassembly 240 against the retainer cap 224. Once seated against the retainer cap 224, further uphole movement by the latching valve subassembly 240 may be arrested.
  • Figure 28 illustrates a cross-sectional view of the vibration tool 200 in accordance with implementations of various techniques described herein. As illustrated, the upper spring 230 may continue to bias the piston subassembly 210 in the uphole direction 201 .
  • the latching valve subassembly 240 may be forced to move from its "open” state to its "closed” state, as illustrated in Figure 28.
  • the balls 292 may begin to traverse in the downhole direction 205 relative to the piston 212, traveling from the second latch stops 282 to the first latch stops 280.
  • Figure 29 illustrates a cross-sectional view of the vibration tool 200 in the "start” position in accordance with implementations of various techniques described herein.
  • the upper spring 230 may bias the piston subassembly 210 back to its "start” position, i.e., into contact with the upper shoulder 234 and/or the top impact surface 264.
  • vibrations may be created throughout the housing 202, which may be imparted to the vibration tool 200 and to a drill string (not shown).
  • the latching valve subassembly 240 may be in its "closed" state. Particularly, since the piston subassembly 210 may continue to move in the uphole direction 201 , the balls 292 may have traversed in the downhole direction 205 relative to the piston 212, traveling from the second latch stops 282 to the first latch stops 280.
  • the fluid flow may again pass from the bore of the upper sub 204 and through the piston bore 214, the nozzle 216, the bore of the lower impact cap 222, and the bore of the lower sub 208. If the fluid flow rate remains greater than or equal to the predetermined threshold flow rate, then the fluid pressure may again increase across the piston 212, leading to an increase in the pressure force acting on the uphole end portion of the piston 212. The vibration tool may then again operate as described with respect to Figures 23-29.
  • the vibration tool 200 may cause the piston subassembly 210 to oscillate in the uphole direction 201 and the downhole direction 205, producing vibrations similar to those produced by the vibration tool 100.
  • FIG. 30 illustrates a cross-sectional view of an impact mitigation subassembly 300 in accordance with implementations of various techniques described herein.
  • the impact mitigation subassembly 300 may include an impact cap 302 and one or more springs 304 disposed within the impact cap 302.
  • the components of the impact mitigation subassembly 300 may be composed of steel or any other implementation known to those skilled in the art.
  • the impact cap 302 may be a hollow cap configured to attach to a downhole end portion of a moving body 400, such as the pistons 1 12 or 212 and/or the lower impact caps 122 or 222.
  • An uphole opening 310 of the impact cap 302 may be used for insertion of the moving body 400, as described in more detail below. Once inserted, the moving body 400 may be seated against or may compress the springs 304 within the impact cap 302.
  • the springs 304 may be disposed on an inside base 312 of the impact cap 302, where the springs 304 may be separated by one or more spacers 306.
  • the springs 304 may include a coiled spring, a Belleville washer spring, or any other biasing mechanism known to those skilled in the art.
  • An anti-erosion sleeve 308 may cover the inner diameters of the springs 304 and/or the spacers 306, and may align with a bore of the moving body 400.
  • the anti-erosion sleeve 308 may allow for fluid to flow from the bore of the moving body 400 and through a downhole opening 314 of the impact cap 302 while protecting the spacers and/or the springs 304.
  • FIG. 31 illustrates a side view of the moving body 400 in accordance with implementations of various techniques described herein.
  • a downhole end portion of the moving body 400 may have one or more locking wings 402 which radially protrude from the moving body 400.
  • In between the locking wings 402 are one or more locking slots 404, formed by the spaces between the locking wings 402.
  • the locking wings 402 and/or the locking slots 404 may be of same size and/or shape.
  • a locking gap 406 may be defined by a space along the moving body 400 and may be uphole relative to the locking wings 402.
  • FIG 32 illustrates a side view of an impact mitigation subassembly 300 in accordance with implementations of various techniques described herein.
  • the uphole opening 310 of the impact cap 302 may include one or more key slots 352 and one or more key wings 354.
  • the key wings 354 may radially protrude from an inner diameter of the uphole opening 310.
  • the key slots 352 may be formed by the spaces between the key wings 354 along the inner diameter of the uphole opening 310.
  • the key wings 354 may align with the locking slots 404 and the key slots 352 may align with the locking wings 402.
  • the key wings 354 may be inserted into the locking slots 404 and the locking wings may be inserted into the key slots 352.
  • the locking gap 406 may have a longitudinal length that is approximately equal to the longitudinal length of the key wings 354. Accordingly, the moving body 400 may be inserted into the impact cap 302 until the key wings 354 occupy the space formed by the locking gap 406. The impact cap 302 may then be rotated so that the key wings 354 are aligned uphole relative to the locking wings 402. Anti-rotation screws may be fastened into screw holes 316 on the impact cap 302 to fasten the impact mitigation subassembly 300 to the moving body 400. In other implementations, other fastening means may be used to couple the impact mitigation subassembly 300 to the moving body 400.
  • the moving body 400 may compress the springs 304 when inserted into the impact cap 302.
  • the springs 304 may provide a predetermined load in the impact mitigation subassembly 300.
  • the impact cap 302 may contact the other object's surface first.
  • a bottom surface 320 may strike the other object's surface upon initial impact.
  • the moving body 400 may continue to move within the impact cap 302, compressing the springs 304.
  • the energy of the moving body may be stored in the springs 304, facilitating rebounding of the impact mitigation subassembly 300.
  • an amount of impact produced by the impact mitigation subassembly 300 may increase with a higher predetermined load.
  • the impact cap 302 may be constructed of steel or any other implementation known to those skilled in the art.
  • a mass of the impact cap 302 may be low enough to reduce impact force and impact-induced stress on impact surfaces, thereby mitigating deformation on the impact surfaces.
  • various implementations described above with respect to Figures 1 -32 may allow for the cyclical increase and decrease in fluid pressure across an piston subassembly of a vibration tool.
  • the cyclical increase and decrease in fluid pressure may cause the piston subassembly to repeatedly strike a housing of the vibration tool, producing vibrations throughout the tool.
  • the vibrations may oscillate the drill string, or other coupled object, and reduce friction.
  • the vibration tool may generate a water hammering effect, such that the vibrations may travel up and down the drill string or other coupled object.
  • the axial vibration may oscillate the drill string, or other coupled object, and reduce friction.

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  • Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Mining & Mineral Resources (AREA)
  • Physics & Mathematics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Fluid Mechanics (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Details Of Valves (AREA)
  • Mechanical Engineering (AREA)

Abstract

L'invention concerne, selon divers modes de réalisation, un outil de vibration destiné, par exemple, à être utilisé lors d'un forage. Selon un mode de réalisation, l'outil de vibration peut comprendre un boîtier au travers duquel s'étend un alésage. L'outil de vibration peut également comprendre un sous-ensemble piston positionné à l'intérieur de l'alésage, le sous-ensemble piston étant configuré pour osciller lorsqu'un écoulement de fluide à l'intérieur du sous-ensemble piston dépasse un débit prédéterminé. L'outil de vibration peut en outre comprendre un mécanisme à soupape positionné autour du sous-ensemble piston, le mécanisme à soupape étant configuré pour limiter l'écoulement d'un fluide à l'intérieur du sous-ensemble piston lorsque le mécanisme à soupape se trouve dans un état fermé et configuré pour permettre l'écoulement du fluide depuis le sous-ensemble piston jusqu'à l'alésage lorsque le mécanisme à soupape se trouve dans un état ouvert.
PCT/US2014/061475 2013-10-31 2014-10-21 Outil de vibration WO2015065755A1 (fr)

Applications Claiming Priority (4)

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US201361898097P 2013-10-31 2013-10-31
US61/898,097 2013-10-31
US14/497,413 2014-09-26
US14/497,413 US20150114716A1 (en) 2013-10-31 2014-09-26 Vibration tool

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105649546A (zh) * 2016-01-07 2016-06-08 西南石油大学 压力脉冲实现稳定冲击作用的井下工具

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10794135B2 (en) * 2017-04-03 2020-10-06 Charles Abernethy Anderson Differential pressure actuation tool and method of use
CN107130919B (zh) * 2017-05-17 2018-11-16 西南石油大学 一种凸轮马达式水力振荡器
CN108301771B (zh) * 2018-04-02 2024-06-14 四川康克石油科技有限公司 一种多功能脉冲装置
CN110005342A (zh) * 2019-04-23 2019-07-12 西南石油大学 射流振荡实现冲击破岩的pdc钻头
CN117823047B (zh) * 2024-03-04 2024-05-14 德州联合石油科技股份有限公司 水力振荡装置
CN117823048B (zh) * 2024-03-05 2024-05-17 德州联合石油科技股份有限公司 水力振荡器

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6152222A (en) * 1996-06-07 2000-11-28 Kveilerorvibrator As Hydraulic device to be connected in a pipe string
US20050230101A1 (en) * 2001-03-01 2005-10-20 Shunfeng Zheng Method and apparatus to vibrate a downhole component
US20050241842A1 (en) * 2004-04-29 2005-11-03 Brent Marsh Reciprocable impact hammer
US20060124292A1 (en) * 2004-12-10 2006-06-15 Victor Bruce M Internal shock absorber plunger
US20100276204A1 (en) * 2009-05-01 2010-11-04 Thru Tubing Solutions, Inc. Vibrating tool

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3568783A (en) * 1969-05-09 1971-03-09 Baker Oil Tools Inc Fluid-actuated impact apparatus
US4434854A (en) * 1980-07-07 1984-03-06 Geo Vann, Inc. Pressure actuated vent assembly for slanted wellbores
US5012871A (en) * 1990-04-12 1991-05-07 Otis Engineering Corporation Fluid flow control system, assembly and method for oil and gas wells

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6152222A (en) * 1996-06-07 2000-11-28 Kveilerorvibrator As Hydraulic device to be connected in a pipe string
US20050230101A1 (en) * 2001-03-01 2005-10-20 Shunfeng Zheng Method and apparatus to vibrate a downhole component
US20050241842A1 (en) * 2004-04-29 2005-11-03 Brent Marsh Reciprocable impact hammer
US20060124292A1 (en) * 2004-12-10 2006-06-15 Victor Bruce M Internal shock absorber plunger
US20100276204A1 (en) * 2009-05-01 2010-11-04 Thru Tubing Solutions, Inc. Vibrating tool

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105649546A (zh) * 2016-01-07 2016-06-08 西南石油大学 压力脉冲实现稳定冲击作用的井下工具

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