Valve for use with downhole tools

An apparatus and method relating to down-hole production equipment for use in an oil well environment is provided. The apparatus and method are for selectively isolating fluid flow through a production packer or other down-hole tubular device. The apparatus and method use a ball valve, which is moved from an open position to a closed position by lateral or axial movement of the tubing string as opposed to by rotating the tubing string.

FIELD

This disclosure relates to down-hole production equipment for use in an oil well environment for selectively isolating fluid flow through a production packer or other down-hole tubular device. More particularly, this disclosure relates to a system and method utilizing a selectively operable valve.

BACKGROUND

Various oil and gas production operations use ball valves. Often packers are used in conjunction with ball valves. The packer closes off the annulus between the tubing string and the well bore or casing. The ball valve can selectively close off the central flow passage of the tubing string such that flow is or is not allowed through the passageway depending on the setting of the ball valve.

The ball valves of the prior art generally disclose use of a spherical ball-valve element, which in a closed valve position has seals, which seal or close off the central flow passageway of the tubing string so that the valve element will seal against pressure in one or both directions. Typically, rotation of the tubing string is used to operate the valve element to move it between open and closed positions. However, rotation is also used to operate other down-hole tools that can be used in conjunction with the ball valve; thus, requiring sequential rotative operations without a positive indication that the valve is fully closed. In addition, in highly deviated well bores, it can be difficult to achieve rotation to set, unset, open or close down-hole tools.

DETAILED DESCRIPTION

Referring now to the drawings, wherein like reference numbers are used herein to designate like elements throughout the various views and various embodiments, which are illustrated and described. The figures are not necessarily drawn to scale, and in some instances the drawings have been exaggerated and/or simplified in places for illustrative purposes only. In the following description, the terms “upper,” “upward,” “up-hole,” “lower,” “downward,” “below,” “down-hole” and the like, as used herein, shall mean: in relation to the bottom or furthest extent of the surrounding wellbore even though the well or portions of it may be deviated or horizontal. The terms “inwardly” and “outwardly” are directions toward and away from, respectively, the geometric center of a referenced object. Where components of relatively well-known designs are employed, their structure and operation will not be described in detail. One of ordinary skill in the art will appreciate the many possible applications and variations of the present invention based on the following description.

Referring now toFIG. 1, a down-hole tool10incorporating the invention is illustrated. Down-hole tool10comprises a valve system. As illustrated the valve system is a ball-valve system12. Additionally, the valve system may contain one or more other tools, such as packer14and tubing16. As illustrated, down-hole tool10is in a well bore18having a casing20. An annulus22is formed between down-hole tool10and casing20. A packer14prevents flow through the annulus22and anchors down-hole tool10in the wellbore, as is known in the art. The packer is shown in an unexpanded position inFIG. 1.

Turning now toFIG. 2, a cross-sectional view of ball-valve system12is illustrated. Ball-valve system12comprises a tubular supporting mandrel24, which has an upper end26adapted to couple to a string of pipe or tubing, or to another down-hole tool. The lower end28of ball-valve system12is also adapted to couple to tubing or another down-hole tool, such as packer14illustrated inFIG. 1. Mandrel24defines a central flow passageway30, which lies upon the longitudinal axis of down-hole tool10. As used herein, longitudinal or axial refers to the long axis of mandrel24extending up-hole to down-hole.

Ball-valve system12generally comprises an actuator section50, a ball-valve section100and a balancing piston section150.FIGS. 3-6illustrate one embodiment of the actuator system50. The actuator system50ofFIGS. 3-6comprises a portion of mandrel24and an outer sleeve51. Outer sleeve51is positioned concentrically about mandrel24and may comprise one or more sleeve portions connected together. Mandrel24and outer sleeve51are in sliding relation so that an axial force on mandrel24will cause it to slide longitudinally in relation to outer sleeve51. Further, this sliding relation is resilient due to spring elements as further described below. Mandrel24has an uppermost position relative to sleeve51wherein spring78is fully expanded under the weight of mandrel24. Mandrel24has a lowermost position defined wherein spring78is compressed. The compression is limited by the movement of a lug in a straight leg channel, described below.

Actuator section50further comprises a tubular member54and a ring68. As shown, tubular member54can be a portion of mandrel24. Tubular member54has a channel58on its outer surface56. Channel58comprises a straight leg section60and a circumferential section62. Straight leg section60extends substantially longitudinally along the surface of tubular member54, as shown inFIG. 4. Circumferential section62extends circumferentially about tubular member54. Circumferential section62has an upper or up-hole surface64and a lower or down-hole surface66. Each surface64and66has a saw tooth configuration.

A ring68is positioned around tubular member54. Ring68is secured against longitudinal movement by coupling Coupling52and sleeve portion53but slidingly engages Coupling52and sleeve portion53. Additionally, ring68slidingly engages mandrel24and its tubular member54. Thus, ring68can rotate about the longitudinal axis of mandrel24. Ring68has a lug70extending inward into channel58. Lug70can be a fixed protuberance on the inner surface of ring68or can be a trapped ball bearing.

When mandrel24slides longitudinally down-hole relative to outer sleeve51, spring78is compressed, thus, biasing mandrel24and tubular member54in an up-hole direction. As can be seen fromFIG. 4, when lug70is positioned in straight leg section60and no axial force is applied to mandrel24, lug70will be in the down-hole most position of straight leg section60due to the biasing effect of spring78. When sufficient axial force is applied to mandrel24, mandrel24will slide in relation to ring68; thus, positioning lug70against upper surface64. Continued axial force, will cause ring68to rotate due to the saw tooth shape of upper surface64. The rotation places lug70in a crest80of upper surface64, as shown inFIG. 5. Releasing the axial force will cause mandrel24to slide longitudinally upward due to the biasing of spring78; thus, lug70will contact lower surface66causing ring68to rotate due to the saw tooth shape of lower surface66. The rotation places lug70in a trough82of lower surface66, as shown inFIG. 6.

Turning now toFIG. 7, the ball-valve section100of ball-valve system12is illustrated. Ball-valve section100includes sleeve portion102of outer sleeve51. Sleeve portion102is connected to sleeve portion53in fixed relation. Within sleeve portion102is a portion of mandrel24, balancing piston152and ball-valve element106. Ball-valve element106is positioned between mandrel24and balancing piston152. A first or top ball seat108is positioned between end110of mandrel24and ball-valve element106to provide sealing engagement and prevent fluid flow from central flow passageway30through the junction of end110and ball-valve element106. Similarly, a second or bottom ball seat111is positioned between end155of balancing piston152and ball-valve element106to provide sealing engagement and prevent fluid flow from central flow passageway30through the junction of end155and ball-valve element106. First and second ball seats108and111can be metal seats that provide a sealing engagement with ball-valve element106.

Ball valve element106has spherical surface portions, which can be sealed against pressure in either direction in a closed condition of the valve, as further described below. Ball-valve element106is rotatable about a rotational axis transverse to the longitudinal axis of down-hole tool10. Ball-valve element106has a flow opening or passage114that extends there through. In a first rotative position or open position, flow opening114is aligned with central flow passageway30, thus allowing flow through central flow passageway30. In a second rotative position or closed position, flow opening114is transverse to central flow passageway30, thus preventing flow through central flow passageway30.

Operating arm116controls the rotation of ball-valve element106. At one end, operating arm has a lug118. Ball-valve element106and operating arm116are attached by positioning lug118in an orifice120. A retainer122traps a second end of operating arm116. Operating arm116and retainer122are positioned between sleeve portion102and balancing piston152. Retainer122slidingly engages sleeve portion102and balancing piston152. The engagement is resilient and biased by spring124in an up-hole direction. Spring124is braced on the down-hole side by a shoulder126formed by ring portion154of balancing piston152.

Thus, retainer122is resiliently restrained from down-hole movement by spring124. Additionally, retainer122is limited in up-hole movement by an offset or shoulder130, best seen fromFIG. 9.

As will be realized from an examination ofFIG. 7, longitudinal movement of mandrel24in a down-hole direction will cause ball-valve element106to move down-hole. While operating arm116will also move down-hole as a result, its movement is resiliently restrained by spring124; thus, it will create an upward force on one side of ball-valve element106by its connection at orifice120. The upward force causes ball-valve element106to rotate from an open position to a closed position. Similarly, from a closed position, upward movement of ball-valve element106will result in operating arm116rotating ball-valve element106from the close position to the open position.

More than one operating arm can be attached to ball-valve element106; thus, as illustrated, there is a second orifice132by which a second operating arm can be attached.

Turning now toFIG. 8, balancing piston section150is illustrated. Balancing piston section150comprises sleeve portions102and128of outer sleeve51, balancing piston152, spring156and lower mandrel158. The lower portion160of balancing piston152is between the upper portion162of lower mandrel158and sleeve portion102. Upper portion162and sleeve portion102slidingly receive balancing piston152so that balancing piston152can move longitudinally up and down-hole. Balancing piston152resiliently slides and is upwardly biased by spring156. Spring156is sandwiched between upper portion162of lower mandrel158and sleeve portion128. At its lower end, spring156is braced by a shoulder164formed on lower mandrel158.

Accordingly, balancing piston152can move downward when mandrel24and ball-valve element106move down-hole and can return upward when they return up-hole. Additionally, at all times balancing piston152is biased upward, and thus asserts pressure on ball-valve element106to maintain the seal of ball seats108and111, and to prevent pressure down-hole of the ball valve from rotating ball-valve element106to an unwanted position. Additionally, when pressure up-hole of the ball valve is greater than the pressure down-hole of the ball, fluid from up-hole can seep into ball-valve element106to prevent the ball valve from being forced into rotation by the up-hole pressure.

With reference now toFIGS. 7 and 10-14, the operation of the down-hole tool will be further described. The ball valve element106being initially in the first rotative position shown inFIGS. 7 and 12, allows flow through central flow passage30defined up-hole of ball valve element106by mandrel24and down-hole of ball-valve element106by balancing piston152and lower mandrel158. In this position, mandrel24is in its upmost longitudinal position and lug70is at the bottom of straight leg section60. Because mandrel24is biased upwardly by spring78, ball-valve element106is locked in the first rotative state until a predetermine force is applied to mandrel24to overcome spring78sufficiently to move ball-valve element106to the second rotative state.

Downward longitudinal force on mandrel24moves ball valve element106to its second rotative position. Typically, the downward longitudinal force or axial force will be exerted upon the mandrel by tubing string or tubing16attached to the upper end26of mandrel24. The axial force is applied by moving tubing16in a down-hole direction in the well bore. Tubing16then asserts the axial force on mandrel24. A packer14or another down-hole tool is attached to lower end28and is anchored in well bore18so as to prevent outer sleeve51from moving down-hole with mandrel24when the axial force is exerted.

As shown inFIGS. 10 and 13, under this axial force mandrel24moves relative to sleeve51and moves downward until lug70comes in contact with upper surface64of circumferential section62. The downward movement of mandrel24transfers the downward force to ball-valve element106, thus moving it downward. Downward force asserted by ball-valve element106on operating arm116is at least partially countered by spring124so that operating arm116moves ball-valve element106to its second rotative position preventing flow through central flow passageway30. Downward force is also asserted by ball-valve element106on balancing piston152. Spring156allows balancing piston152to move downward with ball-valve element106while still maintaining upward pressure such that ball seats108and111maintain a fluid tight seal, hence prevention fluid in central flow passageway30from circumventing ball-valve element106.

As explained above, contact of lug70with upper surface64causes ring68to rotate until lug70is in crest80. Subsequently, the longitudinal force is released causing mandrel24to move upward. However, because lug70now moves into contact with lower surface66of circumferential section62, mandrel24does not return to its uppermost position relative to sleeve51; thus, ball-valve element106remains in the second rotative position. Contact of lug70with lower surface66causes ring68to rotate until lug70is in trough82locking ring68from further rotation without application of further downward longitudinal force. Thus, ball-valve element is now locked in the second rotative position as best seen inFIGS. 11 and 14.

As will be noted fromFIGS. 11 and 14, balancing piston152allows limited movement of ball-valve element106away from first ball seat108when up-hole pressure from the ball-valve element is greater than down-hole pressure from the ball-valve element. Thus, fluid from up-hole can enter flow opening114. This allows the pressure within ball-valve element106to equalize with the portion of central flow passageway30up-hole from ball-valve element106. This can prevent fluid pressure from up-hole forcing ball-valve element106out of its second rotative state.

If the predetermined longitudinal force is again applied to mandrel24, then ring68again rotates due to interaction action of lug70and upper surface64. When the force is released, lug70will now contact a section of lower surface66that slopes down to straight leg section60. Accordingly, ring68will rotate due to interaction of lug70and lower surface66until lug70enters straight leg section60. At this point, spring78will be able to return mandrel24to its uppermost position relative to sleeve51allowing ball-valve element106to also move up and simultaneously rotate back to its first rotative position. It will be appreciated that the embodiments described herein move the ball-valve between a position allowing fluid flow and a position preventing fluid flow with only longitudinal movement (axial movement) of the mandrel and without rotational movement of the mandrel.

Turning now toFIGS. 15-24, a second embodiment of the ball-valve system12is illustrated.FIG. 15illustrates an isometric view of the ball-valve system12andFIG. 16illustrates a cross-sectional view. Like the previous embodiment, ball-valve system12ofFIGS. 15 and 16has an actuator section200, a ball-valve section100and a balancing piston section150. Ball-valve section100and balancing piston section150are substantially as described above.

Turning now toFIGS. 17-24, the actuator system200is illustrated. The actuator system200comprises a portion of mandrel24and an outer sleeve51. Outer sleeve51is positioned concentrically about mandrel24. Mandrel24and outer sleeve51are in sliding relation so that an axial force on mandrel24will cause it to slide longitudinally in relation to outer sleeve51. Further, this sliding relation is resilient due to spring elements.

Mandrel24terminates in a prod member202. Prod member202has a lower angled surface203, which contacts a ring204when mandrel24is in its uppermost position relative to sleeve51. Ring204is sandwiched between and is in sliding relation with a second mandrel206. Second mandrel206is in sliding relation with outer sleeve51and is in sealing contact with ball-valve element106by means of first ball seat108. Accordingly, downward force on mandrel24causes it to slide down-hole and transfers the force via prod member202to ring204. Ring204in response moves down-hole pushing against a shoulder208of second mandrel206, which in turn moves down-hole and pushes against ball-valve element106. As can be seen fromFIG. 17, a spring78biases mandrel24towards an uppermost position relative to mandrel51, as previously described.

Actuator section200further comprises a tubular member210, which is fixedly secured to outer sleeve51. As can best be seen fromFIG. 18-21, tubular member210has a channel212formed from a straight leg section214and a circumferential section216. Straight leg section214extends substantially longitudinally along the surface of tubular member210. Circumferential section216extends circumferentially about tubular member210. In this embodiment, circumferential section216consists of only upper surface218. Upper surface218has a saw tooth configuration.

Ring204can both longitudinally move and can rotate about the longitudinal axis of down-hole tool10. Ring204has an upper ring surface218that is saw tooth in shape, as best seen fromFIG. 19. Ring204has a lug220extending upward along its outer surface to interact with channel212. Lug220has an upper angled surface222, which forms a part of upper ring surface218.

When mandrel24slides longitudinally, down-hole relative to outer sleeve51, spring78is compressed; thus, mandrel24is biased in an up-hole direction. As can be seen fromFIG. 18, when lug220is positioned in straight leg section214and no axial force is applied to mandrel24, lug220will be in the uppermost position of straight leg section214and upper angled surface220will be in contact with lower angled surface203of prod member202due to the biasing effect of spring156.

When sufficient axial force is applied to mandrel24, mandrel24will slide longitudinally down-hole and prod member202will push ring204; thus, moving lug220downward until it is adjacent to upper surface218, as shown inFIG. 19. Due to the angles on lower angled surface203and upper angled surface222, ring204will rotate. The rotation places upper angled222of lug220in contact with upper surface218. Prod member202comes in contact with a trough228in upper ring surface226. Upon release of the axial force, prod member202moves upwards allowing ring204to move upward. Because of the contact between the upper angled surface222of lug220and upper surface218, ring204is further rotated until upper angled surface222is in a crest224of upper surface218, as shown inFIG. 20. Thus, ring204is locked in position until another axial force of sufficient magnitude is applied to mandrel24. When such an axial force is applied, prod member202will come into contact with upper ring surface226and push ring204downward until lug220is free from crest224, as shown inFIG. 21. Ring204will then rotate due to the interaction of lower angled surface203of prod member202with the saw tooth surface of upper ring surface226. The rotation repositions lug220to a portion of upper surface218that is angled toward straight leg section214. When the axial force is released, lug220will be directed to enter straight leg section214by the interaction of upper surface222of lug220with upper surface218.

The operation of the ball-valve element can be seen fromFIGS. 22 to 24. Its operation is substantially as described above for the first embodiment, except that second mandrel206is in contact with ball-valve element106instead of mandrel24.

As will be realized from the above disclosure, the disclosed ball-valve system provides for opening and closing the ball valve with only up and down movement of the mandrel and of the tubing connected to the mandrel's up-hole end. By eliminating the rotation of the tubing, the ball-valve system can provide a better and easier method to open and close a ball valve in a highly deviated well bore than provided by the use of ball valves relying on rotational movement of the tubing string to move between open and closed positions.

In accordance with the above disclosure, various embodiments are now further described. In a first embodiment, a ball-valve system for use in a well casing is provided. The ball-valve system comprises a mandrel, a ball valve and an actuator. The mandrel defines a flow passageway extending longitudinally along a central axis of the mandrel. The ball valve is disposed within the mandrel. The ball valve includes a generally spherically shaped ball-valve element with a flow opening. The ball-valve element has a first rotative position in which the flow opening is aligned with the flow passageway thus allowing flow through the flow passage, and a second rotative position in which the flow opening is transverse to the flow passageway thus preventing flow through the flow passageway. The actuator comprises a tubular member and a ring. The ring engages the tubular member in a sliding relation relationship such that the tubular member and ring have an actuating movement. The actuating movement is a predetermined amount of relative longitudinal movement between the tubular member and the ring sufficient to move the ball-valve element between the first rotative position and the second rotative position. The actuating movement results in relative rotational movement of the tubular member and the ring. The relative rotational movement moves the ball-valve system between a first state in which the ball-valve element is locked in the first rotative position and a second state in which the ball-valve element is locked in the second rotative position. Generally, the actuator moves the ball-valve element between the first rotational position and second rotational position without rotational movement of the mandrel.

In another embodiment, the ring can have a lug that travels in a channel of the tubular member. The channel comprises a straight longitudinal section and a circumferential section. The application and release of axial force moves the lug between the straight leg section and the circumferential section. The circumferential section can have an up-hole surface and a down-hole surface. In this embodiment, when the lug is in the straight longitudinal section, application of axial force on the tubular member causes the actuation movement, which places the lug in contact with the up-hole surface. This contact results in the relative rotational movement such that release of the axial force places the lug in contact with the down-hole surface. The contact with the down-hole surface locks the ball-valve element into the second rotative position. When the lug is in contact with the down-hole surface, application of axial force on the tubular member causes the actuation movement, which places the lug in contact with the up-hole surface. Contact with the up-hole surface results in the relative rotational movement such that release of the axial force places the lug into the straight longitudinal section such that the ball-valve element is locked into the first rotative position. The tubular member can form part of the mandrel and the application of axial force can be on the mandrel.

In a further embodiment, the circumferential section has an up-hole surface. The ring has an angled upper surface and further comprises a prod member with an angled lower surface. In this embodiment, when the lug is in the straight longitudinal section, application of axial force on the prod member causes the lower angled surface of the prod member to interact with a portion of the upper angled surface of the ring on the lug. This interaction causes the actuation movement and the relative rotational movement such that the lug is placed into contact with the up-hole surface of the circumferential section to lock the ball-valve element in the second rotative position. When the lug is in contact with the up-hole surface, application of axial force on the prod member causes the lower angled surface of the prod member to interact with the upper angled surface of the ring. The interaction with the upper angled surface causes the actuation movement and relative rotational movement such that the lug is moved from contact with the up-hole angled surface into the straight longitudinal section to lock the ball-valve element in the first rotative position. The prod member can be part of the mandrel and the application of axial force can be on the mandrel.

Additionally, the ball valve system of the above embodiments can further comprise a first spring disposed around the mandrel such that the first spring biases the relative longitudinal movement of the ring and the tubular member such that the lug is biased in an up-hole direction.

The ball valve systems of the above embodiments can further comprise a balancing piston positioned down-hole of the ball valve. The balancing piston resiliently provides pressure to the ball-valve element to counteract fluid pressure in the flow passageway down-hole from the ball-valve element to thus prevent the fluid pressure from moving the ball-valve element from the second rotative position.

The ball-valve system of the above embodiment can also comprise an operating arm slidingly engaging the balancing piston and an outer sleeve. The operating arm and ball-valve element are attached so that the operating arm resiliently moves the ball-valve element between the first rotative position and the second rotative position in response to the relative axial movement of the ring and tubular member. Further, the operating arm can have a lug and be attached to the ball-valve element by positioning the lug in an orifice in the ball-valve element.

In addition, in the above embodiments the ball-valve element has an interior chamber such that, in the second rotative position, the interior chamber can be in fluid flow communication to a portion of the flow passageway up-hole from the ball valve when an up-hole pressure in the flow passageway above the ball valve exceeds a down-hole pressure in the flow passageway below the ball valve.

In a further embodiment, a method of operating down-hole tool having a ball valve in a well bore is provided. The method comprises:

introducing the down-hole tool into the well bore;

moving a ring and a tubular member longitudinally relative to each other, wherein the ring and the tubular member are in sliding relationship to each other;

moving the ball valve between a first rotative and a second rotational position in reaction to the longitudinal movement of the ring and tubular member, wherein the first rotative position allows flow through a flow passageway of the down-hole tool and the second rotative position prevents flow through the flow passageway; and

moving the ring and the sleeve rotationally relative to each other, wherein the relative rotational movement of the tubular member and the ring moves the down-hole tool between a first state in which the ball valve is not locked in the second rotative position and a second state in which the ball valve is locked in the second rotative position.

In some embodiments, the ring has a lug that travels in a channel of the tubular member. In these embodiments, the method further comprises applying axial force to cause the relative longitudinal movement and the relative rotational movement such that the lug is moved between a straight leg section of the channel and a circumferential section of the channel.

In a portion of the embodiments using the lug and channel, the method further comprises:

applying a first axial force so as to cause the relative longitudinal movement such that the lug is moved along a straight leg section of the channel and placed in contact with an up-hole surface of a circumferential section of the channel such that the contact with the up-hole surface results in the relative rotational movement, wherein the relative longitudinal movement moves the ball-valve element from the first rotative position to the second rotative position;

releasing the first axial force such that the lug comes into contact with a down-hole surface of the circumferential section such that the ball-valve element is locked into the second rotative position;

applying a second axial force so as to cause the relative longitudinal movement such that the lug is moved from contact with the down-hole surface and placed in contact with an up-hole surface such that the contact with the up-hole surface results in the relative rotational movement; and

releasing the second axial force such that the lug enters the straight leg section and the ball-valve element is moved into the second rotative position.

In another portion of the embodiments using the lug and channel, the circumferential section has an up-hole surface, the ring has an angled surface with a portion of the angled upper surface being on the lug, and the method further comprises:

applying a first axial force on the prod member such that an angled surface of the prod member to interact with the portion of the angled surface of the ring so as to cause the relative longitudinal movement such that a lug on the ring travels in a straight leg channel on the tubular member, wherein the relative longitudinal movement moves the ball valve from the first rotative position to the second rotative position, and when the portion of the angled surface on the lug is aligned with an angled surface on the tubular member, the angled surface of the prod and the angled surface of the ring cause relative rotational movement placing the portion of the angled surface on the ring in contact with the angled surface of the tubular member;

releasing the first axial force such that the lug is in locked contact with the angled surface of the tubular member thus locking the ball valve into the second rotative position;

applying a second axial force on the prod member such that the angled surface of the prod member interacts with the angled surface of the ring so as to disengage the lug from locked contact with the angled surface of the tubular member so as to cause the relative rotational movement and align the lug with the straight leg channel; and

releasing the second axial force on the prod member such that the lug travels into the straight line channel with the ring and tubular member undergoing the relative longitudinal movement, which moves the ball valve from the second rotative position to the first rotative position.

Further embodiments of the method can comprise resiliently providing pressure, typically from one or more springs, to the ball valve to counteract fluid pressure in the flow passageway down-hole from the ball valve. Thus, this counteracting pressure prevents the ball valve from moving out of the second rotative position due to the down-hole fluid pressure. Also, the ball valve can resiliently move between the first rotative position and the second rotative position in response to the relative axial movement of the ring and tubular member by an operating arm attached to the ball valve. Also, the operating arm can have a lug, which is attached to the ball valve by positioning the lug in an orifice in the ball valve. In addition, in the above embodiments the ball-valve element can have a flow opening such that, in the first rotative position, the interior flow opening can be in fluid flow communication to a portion of the flow passageway up-hole from the ball valve when an up-hole pressure in the portion of flow passageway up-hole from the ball valve exceeds a down-hole pressure in a portion of the flow passageway down-hole from the ball valve.

Other embodiments will be apparent to those skilled in the art from a consideration of this specification or practice of the embodiments disclosed herein. Thus, the foregoing specification is considered merely exemplary with the true scope thereof being defined by the following claims.