Abstract
A circulating downhole tool utilising a variable fluid pressure regulated cycle valve device that can be attached to the borehole assembly BHA of a coiled tubing and used down an offshore or onshore wellbore is disclosed. The circulating downhole tool utilising a variable fluid pressure regulated cycle valve device can be remotely operated by an operator on the surface as many times as required in either the through-flow, intermediary or circulatory modes-of-operation, by simply varying the drilling fluid flow rate and pressure being supplied from the pump located on the surface and interconnected to the coiled tubing and the BHA that will include the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device.
Claims
1. A circulating downhole tool for selectively diverting fluid to one of: below the circulating downhole tool; or into an annulus between the circulating downhole tool and a wellbore; wherein the tool comprises a cycle valve device that is cyclable utilising a change in pressure above and/or below a pre-determined fluid pressure to trigger the cycle valve device to vary fluid flow diversion cyclically between below the tool or the annulus; and wherein the tool is configured to be remotely operated from surface by an operator to allow selective and unlimited activation of the tool without having to be tripped or pulled out of the wellbore.
2. The tool of claim 1, wherein the tool is configured to selectively open and close one or more side ports by a rotational movement, the rotational movement being responsive to a longitudinal movement of at least a portion of the tool, the longitudinal movement being associated with or triggered by a change in fluid flow or pressure, such as by turning on or off a pump.
3. The tool of claim 1, wherein the cycle valve device comprises a variable fluid pressure regulated cycle valve device with a continuous circumferential patterned cam groove for cyclical relative rotation in response to cyclical longitudinal movement, the cyclical relative rotation configured to cause a cyclic opening and closing of one or more side ports thereby allowing the tool to be endlessly cyclable between configurations for diverting fluid respectively into either below the circulating tool or the annulus; and wherein the patterned cam groove is unidirectional such that the relative rotation is in a single direction, such as a clock-wise direction.
4. (canceled)
5. The tool of claim 2, wherein the rotational movement is configured to divert fluid through either the one or more side ports or through a throughbore to below the circulating tool according to a rotational position of the portion of the tool.
6. The tool of claim 1, wherein the tool is configured to be cycled between three modes of operation: a through-flow mode of operation whereby all fluid is diverted to below the circulating tool; a circulatory mode of operation whereby all fluid is diverted to the annulus; and an intermediary mode of operation whereby a portion of fluid flow is diverted to below the circulating tool and a portion of fluid flow is simultaneously diverted to the annulus.
7. The tool of claim 1, wherein the tool comprises a longitudinal length of less than 50 cm; optionally 30 cm or less; and wherein the tool is configured to operate above milling or jetting tools in a Bottom Hole Assembly.
8. (canceled)
9. The tool of claim 1, wherein the tool is configured to be cycled to a configuration whereby fluid flow is prevented, both to the annulus and to below the circulating tool.
10. The tool of claim 1, wherein the tool comprises a maximised internal diameter to enable maximum drilling fluid velocity and/or turbulent flow in the annulus for more efficient drilling debris removal to the surface when operating in the circulatory mode of operation.
11. The tool of claim 1, wherein the tool is configured to be immune to variations in temperature, pressure, drilling mud type and density, and operating wellbore angle.
12. The tool of claim 1, wherein the tool is configured to be operable and/or activatable by a fluid selected from one or more of: a drilling fluid; nitrogen; an injection fluid; a stimulation fluid; and an acid; and wherein the tool is designed to be Nitrogen and drilling fluid compatible so that either can be delivered to the circulating downhole tool.
13. (canceled)
14. A downhole assembly comprising the tool of claim 1.
15. The downhole assembly of claim 14, wherein the assembly comprises a toolstring with the tool and at least a portion of coiled tubing and/or at least a portion of jointed pipe, such as in a drill-string.
16. A method of selectively circulating fluid downhole, the method comprising: diverting fluid to one of: below a circulating downhole tool; or into an annulus between the circulating downhole tool and a wellbore; remotely operating a downhole circulating tool from surface by an operator without the tool having to be tripped or pulled out of the wellbore; changing a fluid pressure to above and/or below a pre-determined fluid pressure to remotely operate a cycle valve device of the tool to selectively divert fluid to the other of below the circulating downhole or into the annulus; and varying fluid flow diversion cyclically between below the tool and the annulus; wherein the method comprises unlimited activation of the tool.
17. The method of claim 16, wherein the method comprises at least one of: a coiled tubing operation and/or an operation with jointed pipe, such as a drill string.
18. The method of claim 16, wherein the method comprises rotational moving at least a portion of the tool in response to a longitudinal movement, the longitudinal movement being associated with or triggered by the changing of the fluid pressure.
19. The method of claim 16, wherein the method comprises one or more of: hydroblasting a BOP cavity and/or or a subsea wellhead; diverse spotting remediation fluid operations; drilling operations; wellbore clean-up operations; blowout preventer (BOP) stack jetting operations; surge pressure reduction; and/or unloading a wellbore with Nitrogen gas.
20. The method of claim 16, wherein the method comprises a kick out of the wellbore in order to ensure that overbalanced drilling is always occurring.
21. The method of claim 16, wherein the method comprises countering loss of circulation; and wherein the method comprises reducing equivalent circulating density (ECD) window considerations at a bottom of the wellbore formation.
22. (canceled)
23. (canceled)
24. The method of claim 16, wherein the method comprises liner running and/or use with auto fill float equipment; and optionally establishing two avenues of high flow rate and high pressure drilling fluid communication between a BHA pipe interior and the annulus; such as to reduce surge pressure in the annulus.
25. The method of claim 16, wherein the method comprises delivering Nitrogen gas to the circulating downhole tool.
Description
BRIEF DESCRIPTION OF THE DRAWINGS
[0129] The proposed invention will now be described in greater detail with reference to the accompanying drawings:
[0130] FIG. 1—Cross-sectional side view of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device.
[0131] FIG. 2—Cross-sectional side view and lower end view A-A of the lower sub-assembly of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device shown in FIG. 1.
[0132] FIG. 3A—The horizontal orientation side view with hidden details of the two-part cycle valve sleeve of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device shown in FIG. 1.
[0133] FIG. 3B—The horizontal orientation lower end view B-B of the two-part cycle valve sleeve with curved notches and short flat-sided teeth only hidden details of the two-part cycle valve sleeve shown in FIG. 3A, of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device shown in FIG. 1.
[0134] FIG. 4—The elongated circumferential side view of the two-part cycle valve sleeve with their two-part cycle valve sleeve lower half keyway and their eight curved notches and eight three-flat-sided teeth patterns on the two-part cycle valve sleeve lower half upper patterned face, and their two-part cycle valve sleeve upper half keyway and their eight curved notches and eight three-flat-sided teeth patterns, of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device shown in FIG. 1.
[0135] FIG. 5A—Cross-sectional side view C-C and lower end view of the cycle valve of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device with the cycle valve orientated 0° about the centre-line axis and from the horizontal and vertical axes, of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device shown in FIG. 1.
[0136] FIG. 5B—Cross-sectional side view D-D and lower end view of the cycle valve of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device with the cycle valve rotated clockwise 22.5° about the centre-line axis and from the horizontal and vertical axes shown in FIG. 5A, of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device shown in FIG. 1.
[0137] FIG. 5C—Cross-sectional side view E-E and lower end view of the cycle valve of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device with the cycle valve rotated clockwise 45° about the centre-line axis and from the horizontal and vertical axes shown in FIG. 5A, of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device shown in FIG. 1.
[0138] FIG. 6A—External side view and lower end view F-F with some hidden details of the cycle valve inserted inside the two-part cycle valve sleeve with the four cycle valve guide pins pressed against the two-part cycle valve sleeve lower half curved notches, of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device shown in FIG. 1.
[0139] FIG. 6B—External side view and lower end view G-G with some hidden details of the cycle valve inserted inside the two-part cycle valve sleeve with the four cycle valve guide pins pressed against the two-part cycle valve sleeve upper half curved notches, of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device shown in FIG. 1.
[0140] FIG. 6C—External side view and lower end view H-H with some hidden details of the cycle valve inserted inside the two-part cycle valve sleeve with the four cycle valve guide pins pressed against the two-part cycle valve sleeve lower half curved notches, of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device shown in FIG. 1.
[0141] FIG. 7—Cross-sectional side view and lower end view I-I of the upper sub-assembly of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device shown in FIG. 1.
[0142] FIG. 8—Cross-sectional cutaway side view of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device operating in the through-flow remotely operated mode-of-operation whilst operating vertically in a wellbore formation and being supplied with high flow rate and high pressure drilling fluid.
[0143] FIG. 9—Cross-sectional cutaway side view of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device operating in the intermediary remotely operated mode-of-operation whilst operating vertically in a wellbore formation and being supplied with low flow rate and low pressure drilling fluid.
[0144] FIG. 10—Cross-sectional cutaway side view of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device operating in the circulatory remotely operated mode-of-operation whilst operating vertically in a wellbore formation and being supplied with high flow rate and high pressure drilling fluid.
DETAILED DESCRIPTION
[0145] The cross-sectional side view of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1 is shown in FIG. 1.
[0146] The cross-sectional side view and lower end view A-A of the lower sub-assembly 2 of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1 is shown in FIG. 2.
[0147] The lower sub-assembly 2 of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1, has a lower sub-assembly lower flat face 3A. The lower sub-assembly lower flat face 3A has a lower sub-assembly lower flat face inner chamfered edge 3B and a lower sub-assembly lower flat face outer chamfered edge 3C.
[0148] The lower sub-assembly 2 of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1 has a lower sub-assembly lower flat face inner chamfered edge hole 4 that is located centrally about the centre-line axis of the lower sub-assembly 2 of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1. The lower sub-assembly lower flat face inner chamfered edge hole 4 interconnects the lower sub-assembly lower flat face inner chamfered edge 3B to the lower sub-assembly lower flat face inner chamfered edge hole cone 12.
[0149] The lower sub-assembly tapered outer threaded section 5 interconnects the lower sub-assembly lower flat face outer chamfered edge 3C to the lower sub-assembly stepped lower outer surface 6A. The lower sub-assembly stepped lower outer surface 6A has a lower sub-assembly stepped lower outer surface radiused upper edge 6B. The lower sub-assembly stepped lower outer surface radiused upper edge 6B is interconnected to the lower sub-assembly O-ring channel radiused lower edge 8A. The lower sub-assembly O-ring channel radiused lower edge 8A is interconnected to the lower sub-assembly O-ring channel 8B. The lower sub-assembly O-ring channel 8B is interconnected to the lower sub-assembly O-ring channel radiused upper edge 8C. The lower sub-assembly O-ring channel radiused upper edge 8C is interconnected to the lower sub-assembly stepped upper outer surface radiused upper edge 6C. The lower sub-assembly stepped upper outer surface radiused upper edge 6C is interconnected to the lower sub-assembly stepped upper outer surface 6D. A lower sub-assembly O-ring 7A is located within the lower sub assembly O-ring channel 8B, as shown in FIG. 2. A lower sub-assembly O-ring gap 71A exists between the lower sub-assembly O-ring 7A and the lower sub-assembly O-ring channel radiused upper edge 8C to allow for the deformation of the lower sub-assembly O-ring 7A when the lower sub-assembly 2 is interconnected to other borehole assembly equipment, not shown in FIG. 2.
[0150] The lower sub-assembly stepped flat face 9A is perpendicular to the lower sub-assembly stepped upper outer surface 6D. The lower sub-assembly stepped flat face outer chamfered edge 9B interconnects the lower sub-assembly stepped flat face 9A to the lower sub-assembly lower outer surface 11A. The lower sub-assembly lower outer surface 11A is shown in FIG. 2 to be connected to the lower sub-assembly intermediary outer surface lower chamfered edge 10A. The lower sub-assembly intermediary outer surface 10B interconnects the lower sub-assembly intermediary outer surface lower chamfered edge 10A and the lower sub-assembly intermediary outer surface upper chamfered edge 10C. The lower sub-assembly intermediary outer surface upper chamfered edge 10C is interconnected to the lower sub-assembly upper flat face outer chamfered edge 27B by the lower sub-assembly upper outer surface 11B, as shown in FIG. 2.
[0151] The lower sub-assembly circular stepped outer holes 13A, 13B, 13C, 13D are located equidistantly and are rotationally separated by 90° about the centre-line axis to one another around the lower sub-assembly upper outer surface 11B, as shown in FIG. 2. The lower sub-assembly circular stepped holes 13A, 13B, 13C, 13D are interconnected to lower sub-assembly tapped intermediary holes 13E, 13F, 13G, 13H, respectively.
[0152] The lower sub-assembly tapped intermediary holes 13E, 13F, 13G, 13H are interconnected to lower sub-assembly inner holes 15A, 15B, 15C, 15D, respectively, as shown in FIG. 2. Lower sub-assembly threaded nozzles 14A, 14B, 14C, 14D are releaseably and securely threaded to the lower sub-assembly tapped intermediary holes 13E, 13F, 13G, 13H, respectively.
[0153] The lower sub-assembly lower flat face inner chamfered edge hole 4, and the lower sub-assembly stepped lower outer surface 6A, and the lower sub-assembly stepped upper outer surface 6D, and the lower sub-assembly O-ring channel 8B, and the lower sub-assembly intermediary outer surface 10B, and the lower sub-assembly lower outer surface 11A, and the lower sub-assembly upper outer surface 11B, are all parallel to one another and to the centre-line axis of the lower sub-assembly 2, as shown in FIG. 2.
[0154] The lower sub-assembly upper flat face 27A has a lower sub-assembly upper flat face outer chamfered edge 27B and a lower sub-assembly upper flat face inner chamfered edge 25B. The lower sub-assembly upper flat face inner chamfered edge tapped hole 26 interconnects the lower sub-assembly upper flat face inner chamfered edge 25B and the lower sub-assembly upper channel inner chamfered edge 25A. The lower sub-assembly upper flat face inner chamfered edge tapped hole 26 is located centrally about the centre-line axis of the lower sub-assembly 2, as shown in FIG. 2. The lower sub-assembly 2 has a lower sub-assembly upper channel 24B that is interconnected to the lower sub-assembly upper channel inner chamfered edge 25A. The lower sub-assembly upper channel 24B has a lower sub-assembly upper channel lower flat face 24A that is interconnected to the lower sub-assembly upper channel lower flat face inner chamfered edge 23, as shown in FIG. 2. The lower sub-assembly upper channel lower flat face inner chamfered edge 23 is interconnected to the lower sub-assembly upper hole 22B. The lower sub-assembly upper hole 22B is located centrally about the centre-line axis of the lower sub-assembly 2, as shown in FIG. 2. The lower sub-assembly upper hole 22B has a lower sub-assembly upper hole lower flat face 22A. The lower sub-assembly upper hole lower flat face 22A is interconnected to the lower sub-assembly middle hole 21B. The lower sub-assembly middle hole 21B is located centrally about the centre-line axis of the lower sub-assembly 2, as shown in FIG. 2. The lower sub-assembly middle hole 21B has a lower sub-assembly middle hole lower flat face 21A. The lower sub-assembly middle hole lower flat face 21A is interconnected to the lower sub-assembly lower hole 19. The lower sub-assembly lower hole 19 is located centrally about the centre-line axis of the lower sub-assembly 2, as shown in FIG. 2. The lower sub-assembly lower hole 19 is interconnected to the lower sub-assembly lower channel 18. The lower sub-assembly lower channel 18 is located centrally about the centre-line axis of the lower sub-assembly 2, as shown in FIG. 2. The lower sub-assembly lower channel 18 has a lower sub-assembly lower channel flat face 30.
[0155] The lower sub-assembly keyway slot 20A is shown in FIG. 2 to have a lower sub-assembly keyway slot outer flat face 20B that is offset from the centre-line axis of the lower sub-assembly 2, as shown in FIG. 2, equal to the radius of the lower sub-assembly upper hole 22B. The lower sub-assembly keyway slot 20A extends from the lower sub-assembly upper hole lower flat face 22A to the lower sub-assembly lower channel 18. The lower sub-assembly keyway slot 20A has lower sub-assembly keyway slot flat side walls 20C, 20D, as shown in the end view A-A of the lower sub-assembly 2, in FIG. 2.
[0156] The end view A-A of the lower sub-assembly 2, as shown in FIG. 2, also shows that the lower sub-assembly lower channel flat face countersunk holes 17A, 17B, 17C, 17D, 28B, 28D, 28F, 28H have been drilled in the lower sub-assembly lower channel flat face 30. The lower sub-assembly lower channel flat face countersunk holes 17A, 17B, 17C, 17D are equidistantly rotationally separated by 45° to the lower sub-assembly lower channel flat face countersunk holes 28B, 28D, 28F, 28H, respectively, on the lower sub-assembly lower channel flat face 30. The lower sub-assembly lower channel flat face countersunk holes 17A, 17B, 17C, 17D, 28B, 28D, 28F, 28H are also all at the same pitch circle diameter on the lower sub-assembly lower channel flat face 30. The lower sub-assembly lower channel flat face countersunk holes 17A, 17B, 17C, 17D, are interconnected to the lower sub-assembly lower channel holes 16A, 16B, 16C, 16D, respectively.
[0157] The lower sub-assembly lower channel flat face countersunk holes 28B, 28D, 28F, 28H are interconnected to the lower sub-assembly lower channel holes 28A, 28C, 28E, 28G, respectively.
[0158] The lower sub-assembly lower channel flat face countersunk holes 17A, 17B, 17C, 17D, 28B, 28D, 28F, 28H and the lower sub-assembly lower channel holes 16A, 16B, 16C, 16D, 28A, 28C, 28E, 28G are offset from and are parallel to the centre-line axis of the lower sub-assembly 2, as shown in FIG. 2.
[0159] The lower sub-assembly lower channel holes 16A, 16B, 16C, 16D are interconnected to and are drilled through into the lower sub-assembly inner holes 15A, 15B, 15C, 15D, respectively, as shown in FIG. 2.
[0160] The lower sub-assembly lower channel holes 28A, 28C, 28E, 28G are interconnected to and are drilled through the lower sub-assembly lower flat face inner chamfered edge hole cone 12 and into the lower sub-assembly lower flat face inner chamfered edge hole 4, as shown in FIG. 2.
[0161] Located centrally on the lower sub-assembly lower channel flat face 30 and located on the centre-line axis of the lower sub-assembly 2, as shown in FIG. 2, is the lower sub-assembly lower channel flat face central countersunk hole 29A. Interconnected to the lower sub-assembly lower channel flat face central countersunk hole 29A is the lower sub-assembly lower channel flat face central hole 29B. The lower sub-assembly lower channel flat face central hole 29B has a lower sub-assembly lower channel flat face central hole flat face 29C.
[0162] The compression spring centralising caps 31A, 31E are shown in the cross-sectional side view of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1, as shown in FIG. 1, to be located at either end of the compression spring 32. The compression spring centralising caps 31A, 31E each have a compression spring centralising cap rear flat face 31B, 31F, respectively. The compression spring centralising caps 31A, 31E also each have a compression spring centralising cap forward stepped face 31C, 31G, respectively. The compression spring centralising caps 31A, 31E also each have a compression spring centralising cap forward chamfered pin 31D, 31H, respectively, as shown in FIG. 1.
[0163] The compression spring centralising cap 31A can be inserted into the lower sub-assembly lower channel flat face central hole 29B until the compression spring centralising cap rear flat face 31B is pressed against the lower sub-assembly lower channel flat face central hole flat face 29C. The outer diameter of the compression spring centralising cap rear flat face 31B and the compression spring centralising cap forward stepped face 31C should be equal to each other. The outer diameter of the compression spring centralising cap rear flat face 31B and the compression spring centralising cap forward stepped face 31C should be smaller in outer diameter than the internal diameter of the lower sub-assembly lower channel flat face central hole 29B and the lower sub-assembly lower channel flat face central hole flat face 29C, to ensure that the compression spring centralising cap 31A can be releaseably pressed into the lower sub-assembly lower channel flat face central hole 29B.
[0164] The outer diameter of the compression spring 32 should be smaller than the internal diameter of the lower sub-assembly lower channel flat face central hole 29B and the outer diameter of the lower sub-assembly lower channel flat face central hole flat face 29C, to ensure that the compression spring 32 can freely extend and contract and be releaseably pressed into the lower sub-assembly lower channel flat face central hole 29B. One end of the compression spring 32 can be inserted into the lower sub-assembly lower channel flat face central hole 29B until one end of the compression spring 32 is pressed along and around the compression spring centralising cap forward chamfered pin 31D, and until one end of the compression spring 32 is pressed against the compression spring centralising cap forward stepped face 31C, as shown in FIG. 1. The internal diameter of the compression spring 32 should be larger than the outer diameter of the compression spring centralising cap forward chamfered pin 31D to ensure that the compression spring 32 can be releaseably pressed around and can freely extend and contract along and around the compression spring centralising cap forward chamfered pin 31D.
[0165] The compression spring centralising caps 31A, 31E are shown in the cross-sectional side view of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1, as shown in FIG. 1, to be located at either end of the compression spring 32. The compression spring centralising caps 31A, 31E each have a compression spring centralising cap rear flat face 31B, 31F, respectively. The compression spring centralising caps 31A, 31E also each have a compression spring centralising cap forward stepped face 31C, 31G, respectively. The compression spring centralising caps 31A, 31E also each have a compression spring centralising cap forward chamfered pin 31D, 31H, respectively, as shown in FIG. 1.
[0166] The compression spring centralising cap 31E can be inserted into the cycle valve lower flat face central hole 56B until the compression spring centralising cap rear flat face 31F is pressed against the cycle valve lower flat face central hole flat face 56C.
[0167] The outer diameter of the compression spring centralising cap rear flat face 31F and the compression spring centralising cap forward stepped face 31G should be equal to each other. The outer diameter of the compression spring centralising cap rear flat face 31F and the compression spring centralising cap forward stepped face 31G should be smaller in outer diameter than the internal diameter of the cycle valve lower flat face central hole 56B and the cycle valve lower flat face central hole flat face 56C to ensure that the compression spring centralising cap 31E can be releaseably pressed into the cycle valve lower flat face central hole 56B.
[0168] The outer diameter of the compression spring 32 should be smaller than the internal diameter of the cycle valve lower flat face central hole 56B and the outer diameter of the cycle valve lower flat face central hole flat face 56C to ensure that the compression spring 32 can freely extend and contract and be releaseably pressed into the cycle valve lower flat face central hole 56B. One end of the compression spring 32 can be inserted into the cycle valve lower flat face central hole 56B until one end of the compression spring 32 is pressed along and around the compression spring centralising cap forward chamfered pin 31H, and until one end of the compression spring 32 is pressed against the compression spring centralising cap forward stepped face 31G, as shown in FIG. 1. The internal diameter of the compression spring 32 should be larger than the outer diameter of the compression spring centralising cap forward chamfered pin 31H to ensure that the compression spring 32 can be releaseably pressed around and can freely extend and contract along and around the compression spring centralising cap forward chamfered pin 31H.
[0169] The horizontal orientation side view with hidden details of the two-part cycle valve sleeve 33A of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1, is shown in FIG. 3A.
[0170] FIG. 3B shows the horizontal orientation lower end view B-B of the two-part cycle valve sleeve 33B with two-part cycle valve sleeve lower half curved notches 37A, 37B, 37C, 37D, 37E, 37F, 37G, 37H, and two-part cycle valve sleeve upper half curved notches 43A, 43B, 43C, 43D, 43E, 43F, 43G, 43H, and two-part cycle valve sleeve lower half short flat-sided teeth 38A, 38B, 38C, 38D, 38E, 38F, 38G, 38H, and two-part cycle valve sleeve upper half short flat-sided teeth 44A, 44B, 44C, 44D, 44E, 44F, 44G, 44H only hidden details of the two-part cycle valve sleeve 33A of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1 shown in FIG. 3A.
[0171] FIG. 3A shows that the two-part cycle valve sleeve 33A has a two-part cycle valve sleeve lower half lower flat face 34A that is perpendicular to the two-part cycle valve sleeve lower half outer surface 35A and the two-part cycle valve sleeve lower half inner surface 35B.
[0172] FIG. 3A and FIG. 3B show that the two-part cycle valve sleeve 33A and 33B, respectively, has a two-part cycle valve sleeve lower half keyway 36A that is located on the two-part cycle valve sleeve lower half outer surface 35A. The two-part cycle valve sleeve lower half keyway 36A is designed to slide tightly and smoothly along the lower sub-assembly keyway slot 20A, as shown in FIG. 1 and FIG. 2, until the two-part cycle valve sleeve lower half lower flat face 34A makes contact with the lower sub-assembly lower channel flat face 30 of the lower sub-assembly 2, as shown in FIG. 1.
[0173] The two-part cycle valve sleeve lower half keyway 36A has a two-part cycle valve sleeve lower half keyway outer flat surface 36B that is designed to be parallel to the lower sub-assembly keyway slot outer flat face 20B, and be offset from the centre-line axis of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1, that is slightly less than the radius of the lower sub-assembly upper hole 22B, as shown in FIG. 1.
[0174] The two-part cycle valve sleeve lower half keyway 36A has a two-part cycle valve sleeve lower half keyway lower flat face 36C that is in-line with the two-part cycle valve sleeve lower half lower flat face 34A. The two-part cycle valve sleeve lower half keyway 36A extends from the two-part cycle valve sleeve lower half keyway lower flat face 36C to the two-part cycle valve sleeve lower half keyway upper flat face 36D, as shown in FIG. 1 and FIG. 3A. FIG. 3A also shows that the distance from the two-part cycle valve sleeve lower half lower flat face 34A to the two-part cycle valve sleeve lower half keyway upper flat face 36D is slightly less than the distance from the two-part cycle valve sleeve lower half lower flat face 34A to the lower edges of the two-part cycle valve sleeve lower curved notches 37A, 37B, 37C, 37D, 37E, 37F, 37G, 37H.
[0175] The two-part cycle valve sleeve lower half keyway 36A has two-part cycle valve sleeve lower half keyway flat side walls 36E, 36F that are parallel to one another and are equidistantly offset from the two-part cycle valve sleeve centreline 36G, as shown in FIG. 3B. The width of the two-part cycle valve sleeve lower half keyway 36A, represented by the distance between the two-part cycle valve sleeve lower half keyway flat side walls 36E, 36F, should be slightly less than the width of the lower sub-assembly keyway slot 20A, represented by the distance between the lower sub-assembly keyway slot flat side walls 20C, 20D, as shown in the end view A-A of the lower sub-assembly 2, as shown in FIG. 2. This will ensure that the two-part cycle valve sleeve lower half keyway 36A will slide releaseably and tightly and smoothly along the lower sub-assembly keyway slot 20A, as shown in FIG. 1 and FIG. 2, and will not rotate when the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1 is being operated.
[0176] In order to ensure that the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1 functions correctly when the fluid pressure, not shown in FIG. 3A and FIG. 3B, is varied, the two-part cycle valve sleeve lower half upper patterned face 34B needs to be accurately machined in order to produce the eight curved notches and eight three-flat-sided teeth pattern 37A, 38A, 39A, 40A, 41A, 37B, 38B, 39B, 40B, 41B, 37C, 38C, 39C, 40C, 41C, 37D, 38D, 39D, 40D, 41D, 37E, 38E, 39E, 40E, 41E, 37F, 38F, 39F, 40F, 41F, 37G, 38G, 39G, 40G, 41G, 37H, 38H, 39H, 40H, 41H, as shown in FIG. 3A and FIG. 4. FIG. 3A shows that the two-part cycle valve sleeve 33A has a two-part cycle valve sleeve upper half upper flat face 51A that is perpendicular to the two-part cycle valve sleeve upper half outer surface 47A and the two-part cycle valve sleeve upper half stepped outer surface 49 and the two-part cycle valve sleeve upper half inner surface 47B.
[0177] The two-part cycle valve sleeve upper half stepped outer surface 49 has a two-part cycle valve sleeve upper half stepped lower flat face 48 that is parallel to the two-part cycle valve sleeve upper half upper flat face 51A, as shown in FIG. 3A.
[0178] FIG. 3A and FIG. 3B shows that the two-part cycle valve sleeve 33A and 33B, respectively, has a two-part cycle valve sleeve upper half keyway 50A that is located on the two-part cycle valve sleeve upper half stepped outer surface 49. The two-part cycle valve sleeve upper half keyway 50A is designed to slide tightly and smoothly along the lower sub-assembly keyway slot 20A, as shown in FIG. 1 and FIG. 2, until the two-part cycle valve sleeve upper half stepped lower flat face 48 makes contact with the lower sub-assembly middle hole lower flat face 21A of the lower sub-assembly middle hole 21B, as shown in FIG. 1. The two-part cycle valve sleeve upper half keyway 50A has a two-part cycle valve sleeve upper half keyway outer flat surface 50B that is designed to be parallel to the lower sub-assembly keyway slot outer flat face 20B, and be offset from the centre-line axis of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1, that is slightly less than the radius of the lower sub-assembly upper hole 22B, as shown in FIG. 1.
[0179] The two-part cycle valve sleeve upper half keyway 50A has a two-part cycle valve sleeve upper half keyway lower flat face 50C that is in-line with the two-part cycle valve sleeve upper half stepped lower flat face 48. The two-part cycle valve sleeve upper half keyway 50A extends from the two-part cycle valve sleeve upper half keyway lower flat face 50C to the two-part cycle valve sleeve upper half keyway upper flat face 50D that is in-line with the two-part cycle valve sleeve upper half upper flat face 51A, as shown in FIG. 1 and FIG. 3A. FIG. 3A also shows that the distance from the two-part cycle valve sleeve upper half upper flat face 51A to the two-part cycle valve sleeve upper half keyway lower flat face 50C and the two-part cycle valve sleeve upper half stepped lower flat face 48 is less than the distance from the two-part cycle valve sleeve upper half upper flat face 51A to the upper edges of the two-part cycle valve sleeve upper curved notches 43A, 43B, 43C, 43D, 43E, 43F, 43G, 43H.
[0180] The two-part cycle valve sleeve upper half keyway 50A has two-part cycle valve sleeve upper half keyway flat side walls 50E, 50F that are parallel to one another and are equidistantly offset from the two-part cycle valve sleeve centreline 36G, as shown in FIG. 3B. The width of the two-part cycle valve sleeve upper half keyway 50A, represented by the distance between the two-part cycle valve sleeve upper half keyway flat side walls 50E, 50F, should be slightly less than the width of the lower sub-assembly keyway slot 20A, represented by the distance between the lower sub-assembly keyway slot flat side walls 20C, 20D, as shown in the end view A-A of the lower sub-assembly 2, as shown in FIG. 2. This will ensure that the two-part cycle valve sleeve upper half keyway 50A will slide releaseably and tightly and smoothly along the lower sub-assembly keyway slot 20A, as shown in FIG. 1 and FIG. 2, and will not rotate when the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1 is being operated.
[0181] In order to ensure that the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1 functions correctly when the fluid pressure, not shown in FIG. 3A and FIG. 3B, is varied, the two-part cycle valve sleeve upper half lower patterned face 51B needs to be accurately machined in order to produce the eight curved notches and eight three-flat-sided teeth pattern 42A, 43A, 44A, 45A, 46A, 42B, 43B, 44B, 45B, 46B, 42C, 43C, 44C, 45C, 46C, 42D, 43D, 44D, 45D, 46D, 42E, 43E, 44E, 45E, 46E, 42F, 43F, 44F, 45F, 46F, 42G, 43G, 44G, 45G, 46G, 42H, 43H, 44H, 45H, 46H, as shown in FIG. 3A and FIG. 4.
[0182] FIG. 3B shows the horizontal orientation lower end view B-B of the two-part cycle valve sleeve 33B with two-part cycle valve sleeve lower half curved notches 37A, 37B, 37C, 37D, 37E, 37F, 37G, 37H, and two-part cycle valve sleeve upper half curved notches 43A, 43B, 43C, 43D, 43E, 43F, 43G, 43H, and two-part cycle valve sleeve lower half short flat-sided teeth 38A, 38B, 38C, 38D, 38E, 38F, 38G, 38H, and two-part cycle valve sleeve upper half short flat-sided teeth 44A, 44B, 44C, 44D, 44E, 44F, 44G, 44H only hidden details of the two-part cycle valve sleeve 33A of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1, as shown in FIG. 3A.
[0183] FIG. 3B clearly shows that the two-part cycle valve sleeve upper half curved notches 43A, 43B, 43C, 43D, 43E, 43F, 43G, 43H hidden details and the two-part cycle valve sleeve upper half short flat-sided teeth 44A, 44B, 44C, 44D, 44E, 44F, 44G, 44H hidden details of the two-part cycle valve sleeve upper half lower patterned face 51B are circumferentially rotationally clock-wise off-set by 22.5° to the two-part cycle valve sleeve lower half curved notches 37A, 37B, 37C, 37D, 37E, 37F, 37G, 37H hidden details and the and two-part cycle valve sleeve lower half short flat-sided teeth 38A, 38B, 38C, 38D, 38E, 38F, 38G, 38H hidden details of the two-part cycle valve sleeve lower half upper patterned face 34B.
[0184] The hidden details of the two-part cycle valve sleeve lower half short diagonal flat-sided teeth 39A, 39B, 39C, 39D, 39E, 39F, 39G, 39H, and the hidden details of the two-part cycle valve sleeve lower half apex of the flat-sided teeth 40A, 40B, 40C, 40D, 40E, 40F, 40G, 40H, and the hidden details of the two-part cycle valve sleeve lower half long diagonal flat-sided teeth 41A, 41B, 41C, 41D, 41E, 41F, 41G, 41H of the two-part cycle valve sleeve lower half upper patterned face 34B, are not shown in FIG. 3B.
[0185] The hidden details of the two-part cycle valve sleeve upper half long diagonal flat-sided teeth 42A, 42B, 42C, 42D, 42E, 42F, 42G, 42H, and the hidden details of the two-part cycle valve sleeve upper half apex of the flat-sided teeth 46A, 46B, 46C, 46D, 46E, 46F, 46G, 46H, and the hidden details of the two-part cycle valve sleeve upper half short diagonal flat-sided teeth 45A, 45B, 45C, 45D, 45E, 45F, 45G, 45H of the two-part cycle valve sleeve upper half lower patterned face 51B, are not shown in FIG. 3B.
[0186] The elongated circumferential side view of the two-part cycle valve sleeve 33A and 33B with their two-part cycle valve sleeve lower half keyway 36A and their eight curved notches and eight three-flat-sided teeth patterns 37A, 38A, 39A, 40A, 41A, 37B, 38B, 39B, 40B, 41B, 37C, 38C, 39C, 40C, 41C, 37D, 38D, 39D, 40D, 41D, 37E, 38E, 39E, 40E, 41E, 37F, 38F, 39F, 40F, 41F, 37G, 38G, 39G, 40G, 41G, 37H, 38H, 39H, 40H, 41H on the two-part cycle valve sleeve lower half upper patterned face 34B, and their two-part cycle valve sleeve upper half keyway 50A and their eight curved notches and eight three-flat-sided teeth patterns 42A, 43A, 44A, 45A, 46A, 42B, 43B, 44B, 45B, 46B, 42C, 43C, 44C, 45C, 46C, 42D, 43D, 44D, 45D, 46D, 42E, 43E, 44E, 45E, 46E, 42F, 43F, 44F, 45F, 46F, 42G, 43G, 44G, 45G, 46G, 42H, 43H, 44H, 45H, 46H, of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1, are shown in FIG. 4.
[0187] FIG. 4 is the equivalent of cutting the two-part cycle valve sleeve 33A through the two-part cycle valve sleeve lower half outer surface 35A and the two-part cycle valve sleeve lower half keyway 36A and the two-part cycle valve sleeve upper half outer surface 47A and the two-part cycle valve sleeve upper half stepped outer surface 49 and the two-part cycle valve sleeve upper half keyway 50A along the two-part cycle valve sleeve centreline 36G, and then laying the cylindrical-shaped two-part cycle valve sleeve 33A out flat, with the outer circumference OC of the two-part cycle valve sleeve lower half outer surface 35A, as shown in FIG. 4.
[0188] The two-part cycle valve sleeve lower half keyway 36A and the two-part cycle valve sleeve upper half keyway 50A are both designed to slide releaseably and tightly and smoothly along the lower sub-assembly keyway slot 20A, as shown in FIG. 1 and FIG. 2. The two-part cycle valve sleeve lower half keyway 36A and the two-part cycle valve sleeve upper half keyway 50A are both designed to ensure that the two-part cycle valve sleeve 33A and 33B, shown in FIG. 3A and FIG. 3B, respectively, are accurately aligned with one another and will not rotate when the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1 is being operated.
[0189] FIG. 4 shows that the elongated circumferential side view of the eight curved notches and eight three-flat-sided teeth pattern 42A, 43A, 44A, 45A, 46A, 42B, 43B, 44B, 45B, 46B, 42C, 43C, 44C, 45C, 46C, 42D, 43D, 44D, 45D, 46D, 42E, 43E, 44E, 45E, 46E, 42F, 43F, 44F, 45F, 46F, 42G, 43G, 44G, 45G, 46G, 42H, 43H, 44H, 45H, 46H on the two-part cycle valve sleeve upper half lower patterned face 51B are the mirror-image of and are circumferentially rotationally clock-wise off-set by 22.5° to the elongated circumferential side view of the eight curved notches and eight three-flat-sided teeth pattern 37A, 38A, 39A, 40A, 41A, 37B, 38B, 39B, 40B, 41B, 37C, 38C, 39C, 40C, 41C, 37D, 38D, 39D, 40D, 41D, 37E, 38E, 39E, 40E, 41E, 37F, 38F, 39F, 40F, 41F, 37G, 38G, 39G, 40G, 41G, 37H, 38H, 39H, 40H, 41H on the two-part cycle valve sleeve lower half upper patterned face 34B. FIG. 3A and FIG. 4 shows that there is a two-part cycle valve sleeve separation gap 52 between the two-part cycle valve sleeve lower half upper patterned face 34B and the two-part cycle valve sleeve upper half lower patterned face 51B. The two-part cycle valve sleeve separation gap 52 needs to be slightly wider than the outer diameter of the four cycle valve guide pins 59A, 60A, 61A, 62A to allow the free movement of the four cycle valve guide pins 59A, 60A, 61A, 62A when required.
[0190] FIG. 5A shows the cross-sectional side view C-C and lower end view of the cycle valve 53A of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1, with the cycle valve 53A orientated 0° about the centre-line axis and from the horizontal and vertical axes.
[0191] FIG. 5B shows the cross-sectional side view D-D and lower end view of the cycle valve 53B of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1, with the cycle valve 53B rotated clockwise 22.5° about the centre-line axis and from the horizontal and vertical axes shown in FIG. 5A.
[0192] FIG. 5C shows the cross-sectional side view E-E and lower end view of the cycle valve 53C of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1, with the cycle valve 53C rotated clockwise 45° about the centre-line axis and from the horizontal and vertical axes shown in FIG. 5A.
[0193] The cycle valve 53A shown in FIG. 5A, and the cycle valve 53B shown in FIG. 5B, and the cycle valve 53C shown in FIG. 5C, have a cycle valve lower flat face 55 that has a cycle valve lower flat face inner chamfered edge 56A, that is located centrally about the centre-line axis of the cycle valves 53A, 53B, 53C of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1. The cycle valve lower flat face inner chamfered edge 56A interconnects the cycle valve lower flat face to the cycle valve lower flat face central hole 56B. The cycle valve lower flat face central hole 56B has a cycle valve lower flat face central hole flat face 56C, as shown in FIG. 5A, FIG. 5B and FIG. 5C.
[0194] The cycle valve 53A shown in FIG. 5A, and the cycle valve 53B shown in FIG. 5B, and the cycle valve 53C shown in FIG. 5C, have a cycle valve lower flat face outer chamfered edge 57A. The cycle valve lower flat face outer chamfered edge 57A is interconnected to the cycle valve outer surface 57B. The cycle valve outer surface 57B is interconnected to the cycle valve upper flat face outer chamfered edge 57C. The cycle valve upper flat face outer chamfered edge 57C is interconnected to the cycle valve upper flat face 58.
[0195] The four cycle valve truncated cone stoppers 54A, 54B, and 54C, 54D, and 54E, 54F, and 54G, 54H are extensions located on the on the cycle valve lower flat face 55, and are rotationally separated by 90° to one another and are located on a pitch circle diameter that is equi-distant between the cycle valve lower flat face inner chamfered edge 56A and the cycle valve lower flat face outer chamfered edge 57A, as shown in FIG. 5A, FIG. 5B and FIG. 5C.
[0196] The cycle valve 53A shown in FIG. 5A, and the cycle valve 53B shown in FIG. 5B, and the cycle valve 53C shown in FIG. 5C, have four cycle valve holes 64A, 64C, 64E, 64G that are interconnected to cycle valve upper flat face countersunk holes 64B, 64D, 64F, 64H, respectively. The cycle valve upper flat face countersunk holes 64B, 64D, 64F, 64H interconnect the four cycle valve holes 64A, 64C, 64E, 64G, respectively, to the cycle valve upper flat face 58, as shown in FIG. 5A, FIG. 5B and FIG. 5C. The four cycle valve through holes 64A, 64C, 64E, 64G and the interconnected cycle valve upper flat face countersunk holes 64B, 64D, 64F, 64H, respectively, interconnect the cycle valve lower flat face 55 to the cycle valve upper flat face 58. The four cycle valve through holes 64A, 64C, 64E, 64G and the interconnected cycle valve upper flat face countersunk holes 64B, 64D, 64F, 64H, respectively, are rotationally separated by 90° to one another and are rotationally separated by 45° to the four cycle valve truncated cone stoppers 54A, 54B, and 54C, 54D, and 54E, 54F, and 54G, 54H, respectively. The four cycle valve through holes 64A, 64C, 64E, 64G and the interconnected cycle valve upper flat face countersunk holes 64B, 64D, 64F, 64H, respectively, are located on a pitch circle diameter that is equi-distant between the cycle valve lower flat face inner chamfered edge 56A and the cycle valve lower flat face outer chamfered edge 57A, as shown in FIG. 5A, FIG. 5B and FIG. 5C.
[0197] The four cycle valve guide pin holes 63A, 63B, 63C, 63D are drilled into the cycle valve outer surface 57B until the pointed ends of the four cycle valve guide pin holes 63A,63B, 63C, 63D are close to but do not penetrate through to the cycle valve lower flat face central hole 56B, as shown in FIG. 5A, FIG. 5B and FIG. 5C. The four cycle valve guide pin holes 63A,63B, 63C, 63D are drilled into the cycle valve outer surface 57B at a distance that is closer to the cycle valve lower flat face 55 than to the cycle valve upper flat face 58, as shown in FIG. 5A, FIG. 5B and FIG. 5C. The four cycle valve guide pin holes 63A, 63B, 63C, 63D are rotationally separated by 90° to one another and are orientated 0° about the centre-line axis and from the horizontal and vertical axes of the lower end view of the cycle valve 53A, as shown in FIG. 5A. Four cycle valve guide pins 59A, 60A, 61A, 62A are securely press-fitted into the four cycle valve guide pin holes 63A, 63B, 63C, 63D, respectively, until the cycle valve guide pin lower face chamfered edge 59E, 60E, 61E, 62E, respectively, are seated in the pointed ends of the four cycle valve guide pin holes 63A,63B, 63C, 63D, respectively. The four cycle valve guide pins 59A, 60A, 61A, 62A have a cycle valve guide pin upper face 59B, 60B, 61B, 62B, respectively, and have a cycle valve guide pin upper face chamfered edge 59C, 60C, 61C, 62C, respectively, and have a cycle valve guide pin outer surface 59D, 60D, 61D, 62D, respectively, and have a cycle valve guide pin lower face chamfered edge 59E, 60E, 61E, 62E, respectively, and have a cycle valve guide pin lower face 59F, 60F, 61F, 62F, respectively. To ensure that the four cycle valve guide pins 59A, 60A, 61A, 62A remain securely attached in the four cycle valve guide pin holes 63A, 63B, 63C, 63D, respectively, when the cycle valve 53A and the cycle valve 53B and the cycle valve 53C are fitted to and are functioning within a circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1 that is being operated in a wellbore formation 85, not shown in FIG. 5A, FIG. 5B and FIG. 5C, it is recommended that an adhesive such as Loctite® be inserted into the four cycle valve guide pin holes 63A,63B, 63C, 63D before the four cycle valve guide pins 59A, 60A, 61A, 62A are securely press-fitted into the four cycle valve guide pin holes 63A,63B, 63C, 63D, respectively, as shown in FIG. 5A, FIG. 5B and FIG. 5C.
[0198] FIG. 5A shows the cross-sectional side view C-C and the lower end view of the cycle valve 53A of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1, with the cycle valve 53A and its four cycle valve guide pins 59A, 60A, 61A, 62A, and its four cycle valve guide pin holes 63A, 63B, 63C, 63D, and its four cycle valve truncated cone stoppers 54A, 54B, and 54C, 54D, and 54E, 54F, and 54G, 54H are all orientated 0° about the centre-line axis and from the horizontal and vertical axes of the lower end view of the cycle valve 53A of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1.
[0199] The lower end view of the cycle valve 53A shown in FIG. 5A also shows that the four cycle valve through holes 64A, 64C, 64E, 64G and the interconnected cycle valve upper flat face countersunk holes 64B, 64D, 64F, 64H, respectively, are rotationally separated by 45° about the centre-line axis and from the horizontal and vertical axes of the lower end view of the cycle valve 53A of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1, and to the four cycle valve guide pins 59A, 60A, 61A, 62A, and the four cycle valve guide pin holes 63A,63B, 63C, 63D, and the four cycle valve truncated cone stoppers 54A, 54B, and 54C, 54D, and 54E, 54F, and 54G, 54H.
[0200] When the cycle valve 53A shown in FIG. 5A is rotated clockwise 22.5° about the centre-line axis and from the horizontal and vertical axes, the cross-sectional side view D-D and the lower end view of the cycle valve 53B of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1 is produced, as shown in FIG. 5B.
[0201] FIG. 5B shows the cross-sectional side view D-D and the lower end view of the cycle valve 53B of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1, with the cycle valve 53B and its four cycle valve guide pins 59A, 60A, 61A, 62A, and its four cycle valve guide pin holes 63A, 63B, 63C, 63D, and its four cycle valve truncated cone stoppers 54A, 54B, and 54C, 54D, and 54E, 54F, and 54G, 54H and the four cycle valve through holes 64A, 64C, 64E, 64G and the interconnected cycle valve upper flat face countersunk holes 64B, 64D, 64F, 64H, respectively, are all rotationally orientated 22.5° clockwise about the centre-line axis, relative to the lower end view of the cycle valve 53A of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1 shown in FIG. 5A.
[0202] When the cycle valve 53A shown in FIG. 5A is rotated clockwise 45° about the centre-line axis and from the horizontal and vertical axes, or when the cycle valve 53B shown in FIG. 5B is rotated clockwise 22.5° about the centre-line axis and from the horizontal and vertical axes, the cross-sectional side view E-E and the lower end view of the cycle valve 53C of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1 is produced, as shown in FIG. 5C.
[0203] FIG. 5C shows the cross-sectional side view E-E and the lower end view of the cycle valve 53C of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1, with the cycle valve 53C and its four cycle valve guide pins 59A, 60A, 61A, 62A, and its four cycle valve guide pin holes 63A, 63B, 63C, 63D, and its four cycle valve truncated cone stoppers 54A, 54B, and 54C, 54D, and 54E, 54F, and 54G, 54H and the four cycle valve through holes 64A, 64C, 64E, 64G and the interconnected cycle valve upper flat face countersunk holes 64B, 64D, 64F, 64H, respectively, are all rotationally orientated 45° clockwise about the centre-line axis, relative to the lower end view of the cycle valve 53A of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1 shown in FIG. 5A.
[0204] FIG. 6A shows the cycle valve 53A inserted inside the two-part cycle valve sleeve 33A with the four cycle valve guide pins 59A, 60A, 61A, 62A pressed against the two-part cycle valve sleeve lower half curved notches 37A, 37C, 37E, 37G, respectively, external side view and lower end view F-F with some hidden details, of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1.
[0205] FIG. 6A shows the cycle valve 53A, as shown in FIG. 5A, is inserted longitudinally inside the two-part cycle valve sleeve 33A, as shown in FIG. 3A. The cycle valve 53A is longitudinally displaced to the left along the centre-line axis by a longitudinal force, not shown in FIG. 6A, so that the cycle valve lower flat face 55 is in-line with the two-part cycle valve sleeve lower half lower flat face 34A, and the four cycle valve guide pins 59A, 60A, 61A, 62A are pressed against the two-part cycle valve sleeve lower half curved notches 37A, 37C, 37E, 37G, respectively, on the two-part cycle valve sleeve lower half upper patterned face 34B. The cycle valve 53A is orientated 0° about the centre-line axis and from the horizontal and vertical axes, as shown in FIG. 5A. It should be noted that the cycle valve 53A should have a cycle valve outer surface 57B outer diameter that is slightly less than the internal diameter of the two-part cycle valve sleeve lower half inner surface 35B and the two-part cycle valve sleeve upper half inner surface 47B. This will ensure that the cycle valve 53A will be able to smoothly rotate and move longitudinally along the centre-line axis when a bi-directional longitudinal force, not shown in FIG. 6A, is applied along the centre-line axis of the cycle valve 53A.
[0206] FIG. 6B shows the cycle valve 53B inserted inside the two-part cycle valve sleeve 33A with the four cycle valve guide pins 59A, 60A, 61A, 62A pressed against the two-part cycle valve sleeve upper half curved notches 43A, 43C, 43E, 43G, respectively, external side view and lower end view G-G with some hidden details, of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1.
[0207] FIG. 6B shows the cycle valve 53B, as shown in FIG. 5B, is inserted longitudinally inside the two-part cycle valve sleeve 33A, as shown in FIG. 3A. The cycle valve 53B is shown in FIG. 6B to have been longitudinally displaced to the right by a longitudinal force, not shown in FIG. 6B, from the cycle valve 53A position shown in FIG. 6A, along the centre-line axis which results in the four cycle valve guide pins 59A, 60A, 61A, 62A to initially slide along the two-part cycle valve sleeve lower half short flat-sided teeth 38A, 38C, 38E, 38G, respectively.
[0208] The four cycle valve guide pins 59A, 60A, 61A, 62A are constrained to travel within the two-part cycle valve sleeve separation gap 52 between the two-part cycle valve sleeve lower half upper patterned face 34B and the two-part cycle valve sleeve upper half lower patterned face 51B, as shown in FIG. 4. In-effect, the two-part cycle valve sleeve separation gap 52 acts as a patterned cam groove in which the four cycle valve guide pins 59A, 60A, 61A, 62A are constrained to travel uni-directionally within when the cycle valve 53B has a longitudinal force, not shown in FIG. 6B, applied to it, that results in the cycle valve 53B to be longitudinally displaced and rotated 22.5° in a uni-directional clock-wise direction about the centre-line axis of and inside the two-part cycle valve sleeve 33A.
[0209] As the cycle valve 53B continues to be longitudinally displaced to the right by a force, not shown in FIG. 6B, along the centre-line axis, this results in the four cycle valve guide pins 59A, 60A, 61A, 62A to press against and then slide along the two-part cycle valve sleeve upper half long diagonal flat-sided teeth 42A, 42C, 42E, 42G, respectively, and towards the two-part cycle valve sleeve upper half curved notches 43A, 43C, 43E, 43G, respectively. The sliding action of the four cycle valve guide pins 59A, 60A, 61A, 62A along the two-part cycle valve sleeve upper half long diagonal flat-sided teeth 42A, 42C, 42E, 42G, respectively, results in the uni-directional 22.5° rotational clock-wise motion of the interconnected cycle valve 53B about the centre-line axis and from the horizontal and vertical axes, as shown in FIG. 5B, until the four cycle valve guide pins 59A, 60A, 61A, 62A are stopped by and are pressed against the two-part cycle valve sleeve upper half curved notches 43A, 43C, 43E, 43G, respectively, as shown in FIG. 6B.
[0210] The cycle valve 53B is longitudinally displaced to the right along the centre-line axis so that the cycle valve lower flat face 55 is longitudinally off-set to the two-part cycle valve sleeve lower half lower flat face 34A. The cycle valve 53B and its four cycle valve guide pins 59A, 60A, 61A, 62A, and its four cycle valve guide pin holes 63A, 63B, 63C, 63D, and its four cycle valve truncated cone stoppers 54A, 54B, and 54C, 54D, and 54E, 54F, and 54G, 54H, and its four cycle valve through holes 64A, 64C, 64E, 64G, and its interconnected cycle valve upper flat face countersunk holes 64B, 64D, 64F, 64H, respectively, as shown in FIG. 5B and FIG. 6B, are rotationally orientated 22.5° clockwise about the centre-line axis and from the horizontal and vertical axes, from the cycle valve 53A and its four cycle valve guide pins 59A, 60A, 61A, 62A, and its four cycle valve guide pin holes 63A, 63B, 63C, 63D, and its four cycle valve truncated cone stoppers 54A, 54B, and 54C, 54D, and 54E, 54F, and 54G, 54H and its four cycle valve through holes 64A, 64C, 64E, 64G and its interconnected cycle valve upper flat face countersunk holes 64B, 64D, 64F, 64H, respectively, as shown in FIG. 5A and FIG. 6A.
[0211] It should be noted that the cycle valve 53B should have a cycle valve outer surface 57B outer diameter that is slightly less than the internal diameter of the two-part cycle valve sleeve lower half inner surface 35B and the two-part cycle valve sleeve upper half inner surface 47B. This will ensure that the cycle valve 53B will be able to smoothly rotate and move longitudinally along the centre-line axis when a bi-directional longitudinal force, not shown in FIG. 6B, is applied along the centre-line axis of the cycle valve 53B.
[0212] FIG. 6C shows the cycle valve 53C inserted inside the two-part cycle valve sleeve 33A with the four cycle valve guide pins 59A, 60A, 61A, 62A pressed against the two-part cycle valve sleeve lower half curved notches 37B, 37D, 37F, 37H, respectively, external side view and lower end view H-H with some hidden details, of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1.
[0213] FIG. 6C shows the cycle valve 53C, as shown in FIG. 5C, is inserted longitudinally inside the two-part cycle valve sleeve 33A, as shown in FIG. 3A. The cycle valve 53C is shown in FIG. 6C to have been longitudinally displaced to the left by a longitudinal force, not shown in FIG. 6C, from the cycle valve 53B position shown in FIG. 6B, along the centre-line axis which results in the four cycle valve guide pins 59A, 60A, 61A, 62A to initially slide along the two-part cycle valve sleeve upper half short flat-sided teeth 44A, 44C, 44E, 44G, respectively. The four cycle valve guide pins 59A, 60A, 61A, 62A are constrained to travel within the two-part cycle valve sleeve separation gap 52 between the two-part cycle valve sleeve lower half upper patterned face 34B and the two-part cycle valve sleeve upper half lower patterned face 51B, as shown in FIG. 4. In-effect, the two-part cycle valve sleeve separation gap 52 acts as a patterned cam groove in which the four cycle valve guide pins 59A, 60A, 61A, 62A are constrained to travel uni-directionally within when the cycle valve 53C has a longitudinal force, not shown in FIG. 6C, applied to it, that results in the cycle valve 53C to be longitudinally displaced and rotated 22.5° in a uni-directional clock-wise direction about the centre-line axis of and inside the two-part cycle valve sleeve 33A.
[0214] As the cycle valve 53C continues to be longitudinally displaced to the left by a force, not shown in FIG. 6C, along the centre-line axis, this results in the four cycle valve guide pins 59A, 60A, 61A, 62A to press against and then slide along the two-part cycle valve sleeve lower half long diagonal flat-sided teeth 41A, 41C, 41E, 41G, respectively, and towards the two-part cycle valve sleeve lower half curved notches 37B, 37D, 37F, 37H, respectively. The sliding action of the four cycle valve guide pins 59A, 60A, 61A, 62A along the two-part cycle valve sleeve lower half long diagonal flat-sided teeth 41A, 41C, 41E, 41G, respectively, results in the uni-directional 22.5° rotational clock-wise motion of the interconnected cycle valve 53C about the centre-line axis and from the horizontal and vertical axes, as shown in FIG. 5C, until the four cycle valve guide pins 59A, 60A, 61A, 62A are stopped by and are pressed against the two-part cycle valve sleeve lower half curved notches 37B, 37D, 37F, 37H, respectively, as shown in FIG. 6C. It should be noted that the cycle valve 53C is longitudinally displaced to the left along the centre-line axis so that the cycle valve lower flat face 55 is in-line with the two-part cycle valve sleeve lower half lower flat face 34A. The cycle valve 53C shown in FIG. 6C is therefore in the same longitudinal position along the centre-line axis inside the two-part cycle valve sleeve 33A, as the cycle valve 53A shown in FIG. 6A.
[0215] However, the cycle valve 53C and its four cycle valve guide pins 59A, 60A, 61A, 62A, and its four cycle valve guide pin holes 63A, 63B, 63C, 63D, and its four cycle valve truncated cone stoppers 54A, 54B, and 54C, 54D, and 54E, 54F, and 54G, 54H, and its four cycle valve through holes 64A, 64C, 64E, 64G, and its interconnected cycle valve upper flat face countersunk holes 64B, 64D, 64F, 64H, respectively, as shown in FIG. 5C and FIG. 6C, are rotationally orientated 45° clockwise about the centre-line axis and from the horizontal and vertical axes, from the cycle valve 53A and its four cycle valve guide pins 59A, 60A, 61A, 62A, and its four cycle valve guide pin holes 63A, 63B, 63C, 63D, and its four cycle valve truncated cone stoppers 54A, 54B, and 54C, 54D, and 54E, 54F, and 54G, 54H, and its four cycle valve through holes 64A, 64C, 64E, 64G, and its interconnected cycle valve upper flat face countersunk holes 64B, 64D, 64F, 64H, respectively, as shown in FIG. 5A and FIG. 6A.
[0216] It should be noted that the cycle valve 53C should have a cycle valve outer surface 57B outer diameter that is slightly less than the internal diameter of the two-part cycle valve sleeve lower half inner surface 35B and the two-part cycle valve sleeve upper half inner surface 47B. This will ensure that the cycle valve 53C will be able to smoothly rotate and move longitudinally along the centre-line axis when a bi-directional longitudinal force, not shown in FIG. 6C, is applied along the centre-line axis of the cycle valve 53C.
[0217] The bi-directional longitudinal movement and uni-directional 22.5° rotational clock-wise cyclical step movement of the cycle valve 53A, 53B, 53C along the centre-line axis inside the two-part cycle valve sleeve 33A, when a bi-directional longitudinal force, not shown in FIG. 6A, FIG. 6B, FIG. 6C, respectively, is applied along the centre-line axis of the cycle valve 53A, 53B, 53C, as described in FIG. 6A, FIG. 6B and FIG. 6C, respectively, is designed to be repeatable for many thousands of cyclical movements of the cycle valve 53A, 53B, 53C over the life-time of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1. This will occur due to the eight curved notches and eight three-flat-sided teeth pattern 42A, 43A, 44A, 45A, 46A, 42B, 43B, 44B, 45B, 46B, 42C, 43C, 44C, 45C, 46C, 42D, 43D, 44D, 45D, 46D, 42E, 43E, 44E, 45E, 46E, 42F, 43F, 44F, 45F, 46F, 42G, 43G, 44G, 45G, 46G, 42H, 43H, 44H, 45H, 46H on the two-part cycle valve sleeve upper half lower patterned face 51B, which are the mirror-image of and are circumferentially rotationally clock-wise off-set by 22.5° to the elongated circumferential side view of the eight curved notches and eight three-flat-sided teeth pattern 37A, 38A, 39A, 40A, 41A, 37B, 38B, 39B, 40B, 41B, 37C, 38C, 39C, 40C, 41C, 37D, 38D, 39D, 40D, 41D, 37E, 38E, 39E, 40E, 41E, 37F, 38F, 39F, 40F, 41F, 37G, 38G, 39G, 40G, 41G, 37H, 38H, 39H, 40H, 41H on the two-part cycle valve sleeve lower half upper patterned face 34B, as shown in FIG. 4. The four cycle valve guide pins 59A, 60A, 61A, 62A are constrained to travel within the two-part cycle valve sleeve separation gap 52 between the two-part cycle valve sleeve lower half upper patterned face 34B and the two-part cycle valve sleeve upper half lower patterned face 51B, as shown in FIG. 4. In-effect, the two-part cycle valve sleeve separation gap 52 acts as a patterned cam groove in which the four cycle valve guide pins 59A, 60A, 61A, 62A are constrained to travel uni-directionally within, when a bi-directional longitudinal force, not shown in FIG. 6A,
[0218] FIG. 6B, FIG. 6C, respectively, is applied along the centre-line axis of the cycle valve 53A, 53B, 53C, as described in FIG. 6A, FIG. 6B and FIG. 6C, respectively. This results in the cycle valve 53A, 53B, 53C to be longitudinally displaced and rotated 22.5° in a uni-directional clock-wise direction about the centre-line axis of and inside the two-part cycle valve sleeve 33A, as shown in FIG. 6A, FIG. 6B and FIG. 6C.
[0219] The cross-sectional side view and lower end view I-I of the upper sub-assembly 66 of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1, is shown in FIG. 7.
[0220] The upper sub-assembly 66 of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1, has an upper sub-assembly lower flat face 67A. The upper sub-assembly lower flat face 67A has an upper sub-assembly lower flat face countersunk hole 67B that is located centrally about the centre-line axis of the upper sub-assembly 66 of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1. The upper sub-assembly lower flat face countersunk hole 67B is interconnected to the upper sub-assembly lower hole 68 that is located centrally about the centre-line axis of the upper sub-assembly 66 of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1, as shown in FIG. 7. The upper sub-assembly lower flat face 67A also has an upper sub-assembly lower flat face outer chamfered edge 67C. The upper sub-assembly lower flat face outer chamfered edge 67C is interconnected to the upper sub-assembly lower outer surface 69A. The upper sub-assembly lower outer surface 69A has an upper sub-assembly lower outer surface radiused upper edge 69B. The upper sub-assembly lower outer surface radiused upper edge 69B is interconnected to the upper sub-assembly O-ring channel radiused lower edge 70A. The upper sub-assembly O-ring channel radiused lower edge 70A is interconnected to the upper sub-assembly O-ring channel 70B. The upper sub-assembly O-ring channel 70B is interconnected to the upper sub-assembly O-ring channel radiused upper edge 70C. The upper sub-assembly O-ring channel radiused upper edge 70C is interconnected to the upper sub-assembly upper outer surface radiused upper edge 69C. The upper sub-assembly upper outer surface radiused upper edge 69C is interconnected to the upper sub-assembly upper outer surface 69D. An upper sub-assembly O-ring 7B is located within the upper sub-assembly O-ring channel 70B. An upper sub-assembly O-ring gap 71B exists between the upper sub-assembly O-ring 7B and the upper sub-assembly O-ring channel radiused upper edge 70C to allow for the deformation of the upper sub-assembly O-ring 7B when the upper sub-assembly 66 is interconnected to the lower sub-assembly 2 of the circulating downhole tool utilizing a variable fluid pressure regulated cycle valve device 1, as shown in FIG. 1.
[0221] The upper sub-assembly upper outer surface 69D is interconnected to the upper sub-assembly stepped lower flat face 72. The upper sub-assembly stepped flat face 72 is perpendicular to the upper sub-assembly upper outer surface 69D. The upper sub-assembly parallel outer threaded section 73 interconnects the upper sub-assembly stepped flat face 72 to the upper sub-assembly intermediary outer surface 74. The upper sub-assembly intermediary outer surface 74 is interconnected to the upper sub-assembly stepped intermediary flat face 75A. The upper sub-assembly stepped intermediary flat face 75A is interconnected to the upper sub-assembly stepped intermediary flat face outer chamfered edge 75B. The upper sub-assembly upper outer surface 76 interconnects the upper sub-assembly stepped intermediary flat face outer chamfered edge 75B and the upper sub-assembly upper flat face outer chamfered edge 81A, as shown in FIG. 7. The upper sub-assembly upper flat face 81B has an upper sub-assembly upper flat face outer chamfered edge 81A and an upper sub-assembly upper flat face inner chamfered edge 81C. The upper sub-assembly upper flat face inner chamfered edge 81C is interconnected to the upper sub-assembly upper hole 80. The upper sub-assembly upper hole 80 is located centrally about the centre-line axis of the upper sub-assembly 66, as shown in FIG. 7. The upper sub-assembly upper hole 80 is interconnected to the upper sub-assembly tapered inner threaded section 79. The upper sub-assembly tapered inner threaded section 79 is interconnected to the upper sub-assembly intermediary hole 78. The upper sub-assembly tapered inner threaded section 79 and the interconnected upper sub-assembly intermediary hole 78 are located centrally about the centre-line axis of the upper sub-assembly 66. The upper sub-assembly intermediary hole 78 is interconnected to the upper sub-assembly intermediary countersunk hole 77. The upper sub-assembly intermediary countersunk hole 77 is interconnected to the upper sub-assembly lower hole 68, as shown in FIG. 7.
[0222] The upper sub-assembly lower hole 68, and the upper sub-assembly lower outer surface 69A, and the upper sub-assembly upper outer surface 69D, and the upper sub-assembly O-ring channel 70B, and the upper sub-assembly parallel outer threaded section 73, and the upper sub-assembly intermediary outer surface 74, and the upper sub-assembly upper outer surface 76, and the upper sub-assembly intermediary hole 78, and the upper sub-assembly upper hole 80, are all parallel to one another and to the centre-line axis of the upper sub-assembly 66, as shown in FIG. 7.
[0223] FIG. 8 shows the cross-sectional cutaway side view of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 82 operating in the through-flow remotely operated mode-of-operation whilst operating vertically in a wellbore formation 85 and being supplied with high flow rate and high pressure drilling fluid 83A.
[0224] FIG. 8 shows the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 82 being supplied with high flow rate and high pressure drilling fluid 83A and being directed by the cycle valve 53A, that is inserted longitudinally inside the two-part cycle valve sleeve 33A, as shown in FIG. 6A, and flowing through the cycle valve upper flat face countersunk holes 64B, 64D, 64F, 64H and the interconnected four cycle valve through holes 64A, 64C, 64E, 64G, respectively, and flowing into the in-line lower sub-assembly lower channel flat face countersunk holes 28B, 28D, 28F, 28H, respectively, and flowing through the interconnected lower sub-assembly lower channel holes 28A, 28C, 28E, 28G, respectively, and flowing into the lower sub-assembly lower flat face inner chamfered edge hole 4, and flowing into a section of the lower borehole assembly that could include a drilling bit, not shown in FIG. 8.
[0225] When the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 82, as shown in FIG. 8, is lowered down the wellbore formation 85 to a pre-determined depth controlled by the operator of the drilling platform, not shown in FIG. 8, the operator of the drilling fluid pump on the drilling platform, not shown in FIG. 8, can at any time remotely operate a change in the mode-of-operation of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1, from the intermediary remotely operated mode-of-operation of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1, as shown in FIG. 1, the configuration of which will be described in more detail in the intermediary remotely operated mode-of-operation of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 86, as shown in FIG. 9, to the through-flow remotely operated mode-of-operation of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 82, as shown in FIG. 8.
[0226] The through-flow remotely operated mode-of-operation of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 82, as shown in FIG. 8, can be accomplished by switching on the drilling fluid pump or increasing the drilling fluid pump flow rate and pressure above a pre-determined drilling fluid flow rate and pressure that will exceed the compression spring compression force characteristics including the spring force constant of the compression spring 32 housed within the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 82, as shown in FIG. 8.
[0227] The lower sub-assembly tapered outer threaded section 5 of the lower sub-assembly 2, as shown in FIG. 2, of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 82, as shown in FIG. 8, will need to be interconnected to a lower borehole assembly tapered inner threaded section, not shown in FIG. 8. The lower borehole assembly tapered inner threaded section, not shown in FIG. 8, could be a section of the lower borehole assembly that could include a drilling bit, not shown in FIG. 8, that will be initially lowered by a drilling platform, not shown in FIG. 8, into the wellbore formation 85.
[0228] The upper sub-assembly tapered inner threaded section 79 of the upper sub-assembly 66, as shown in FIG. 7, of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 82, as shown in FIG. 8, will need to be interconnected to an upper borehole assembly tapered inner threaded section, not shown in FIG. 8. The upper borehole assembly tapered inner threaded section, not shown in FIG. 8, could be a section of the upper borehole assembly that could include coiled tubing, not shown in FIG. 8, that will be uncoiled and lowered by a drilling platform, not shown in FIG. 8, into the wellbore formation 85.
[0229] The drilling fluid pump on the drilling platform, not shown in FIG. 8, will pump high flow rate and high pressure drilling fluid 83A into the section of the upper borehole assembly that could include coiled tubing, not shown in FIG. 8, that will be uncoiled and lowered by a drilling platform, not shown in FIG. 8, into the wellbore formation 85. The high flow rate and high pressure drilling fluid 83A will then flow into the interconnected upper-assembly 66 of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 82.
[0230] FIG. 8 shows the high flow rate and high pressure drilling fluid 83A flowing through the upper sub-assembly lower hole 68 and through the interconnected upper sub-assembly lower flat face countersunk hole 67B. The high flow rate and high pressure drilling fluid 83A then flows onto and presses against the cycle valve upper flat face 58 of the cycle valve 53A that is inserted inside the two-part cycle valve sleeve 33A. The cycle valve 53A has been longitudinally displaced along the centre-line axis by the longitudinal force of the high flow rate and high pressure drilling fluid 83A that flows onto and presses against the cycle valve upper flat face 58 of the cycle valve 53A that is inserted inside the two-part cycle valve sleeve 33A, as shown in FIG. 6A and FIG. 8. This occurs as the high flow rate and high pressure drilling fluid 83A, as shown in FIG. 8, that flows onto and presses against the cycle valve upper flat face 58 of the cycle valve 53A that is inserted inside the two-part cycle valve sleeve 33A, as shown in FIG. 6A and FIG. 8, exceeds a pre-determined drilling fluid flow rate and pressure that exceeds the compression spring compression force characteristics including the spring force constant of the compression spring 32. This results in the compression of the compression spring 32, as shown in FIG. 8, as the compression spring centralising cap 31E that is located inside the cycle valve lower flat face central hole 56B and is pressed against the cycle valve lower flat face central hole flat face 56C, has been longitudinally displaced along the centre-line axis with the cycle valve 53A, towards the compression spring centralising cap 31A, that is inserted into the lower sub-assembly lower channel flat face central hole 29B and which presses against the lower sub-assembly lower channel flat face central hole flat face 29C, as shown in FIG. 8.
[0231] The cycle valve lower flat face 55 is in-line with the two-part cycle valve sleeve lower half lower flat face 34A and is pressing against the lower sub-assembly lower channel flat face 30, as shown in FIG. 8. FIG. 6A and FIG. 8 also show that the four cycle valve guide pins 59A, 60A, 61A, 62A are pressed against the two-part cycle valve sleeve lower half curved notches 37A, 37C, 37E, 37G, respectively, on the two-part cycle valve sleeve lower half upper patterned face 34B. The cycle valve 53A in FIG. 6A and FIG. 8 is orientated 0° about the centre-line axis and from the horizontal and vertical axes, as shown in FIG. 5A.
[0232] FIG. 5A shows that the four cycle valve truncated cone stoppers 54A, 54B, and 54C, 54D, and 54E, 54F, and 54G, 54H, are extensions located on the cycle valve lower flat face 55. FIG. 6A shows that the four cycle valve truncated cone stoppers 54A, 54B, and 54C, 54D, and 54E, 54F, and 54G, 54H are longitudinally displaced along the centre-line axis and to the left past the two-part cycle valve sleeve lower half lower flat face 34A. FIG. 8 shows that the two-part cycle valve sleeve lower half lower flat face 34A is pressed against the lower sub-assembly lower channel flat face 30. FIG. 8 also shows that the four cycle valve truncated cone stoppers 54A, 54B, and 54C, 54D, and 54E, 54F, and 54G, 54H are pressed against and are seated within the lower sub-assembly lower channel flat face countersunk holes 17A, 17B, 17C, 17D, respectively, and the interconnected lower sub-assembly lower channel holes 16A, 16B, 16C, 16D, respectively, which blocks the high flow rate and high pressure drilling fluid 83A from flowing through the lower sub-assembly lower channel flat face countersunk holes 17A, 17B, 17C, 17D, and the interconnected to the lower sub-assembly lower channel holes 16A, 16B, 16C, 16D, respectively, and the interconnected lower sub-assembly inner holes 15A, 15B, 15C, 15D, respectively, and the interconnected lower sub-assembly threaded nozzles 14A, 14B, 14C, 14D, respectively, as shown in FIG. 8. This occurs as the cycle valve 53A, as shown in FIG. 5A and FIG. 8, has its four cycle valve guide pins 59A, 60A, 61A, 62A, and its four cycle valve guide pin holes 63A, 63B, 63C, 63D, and its four cycle valve truncated cone stoppers 54A, 54B, and 54C, 54D, and 54E, 54F, and 54G, 54H, are all orientated 0° about the centre-line axis and from the horizontal and vertical axes of the lower end view of the cycle valve 53A of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 82 shown in FIG. 8.
[0233] However, the high flow rate and high pressure drilling fluid 83A is able to flow freely through the cycle valve upper flat face countersunk holes 64B, 64D, 64F, 64H and the interconnected four cycle valve through holes 64A, 64C, 64E, 64G, respectively, as the lower end view of the cycle valve 53A, as shown in FIG. 5A, shows that the four cycle valve through holes 64A, 64C, 64E, 64G and the interconnected cycle valve upper flat face countersunk holes 64B, 64D, 64F, 64H, respectively, are rotationally separated by 45° about the centre-line axis and from the horizontal and vertical axes of the lower end view of the cycle valve 53A of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 82, and to the four cycle valve guide pins 59A, 60A, 61A, 62A, and the four cycle valve guide pin holes 63A,63B, 63C, 63D, and the four cycle valve truncated cone stoppers 54A, 54B, and 54C, 54D, and 54E, 54F, and 54G, 54H. The high flow rate and high pressure drilling fluid 83A is then able to flow freely through the four cycle valve through holes 64A, 64C, 64E, 64G and into the in-line lower sub-assembly lower channel flat face countersunk holes 28B, 28D, 28F, 28H, respectively, on the lower sub-assembly lower channel flat face 30 of the lower sub-assembly 2, as shown in FIG. 8. The high flow rate and high pressure drilling fluid 83A is then able to flow freely into the interconnected lower sub-assembly lower channel holes 28A, 28C, 28E, 28G, respectively. The lower sub-assembly lower channel holes 28A, 28C, 28E, 28G are interconnected to and are drilled through the lower sub-assembly lower flat face inner chamfered edge hole cone 12 and into the lower sub-assembly lower flat face inner chamfered edge hole 4, as shown in FIG. 2 and FIG. 8. The high flow rate and high pressure drilling fluid 83A is then able to flow freely into the lower sub-assembly lower flat face inner chamfered edge hole 4 of the lower sub-assembly 2.
[0234] The lower sub-assembly tapered outer threaded section 5 of the lower sub-assembly 2, as shown in FIG. 2, of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 82, as shown in FIG. 8, will need to be interconnected to a lower borehole assembly tapered inner threaded section, not shown in FIG. 8. The lower borehole assembly tapered inner threaded section, not shown in FIG. 8, could be a section of the lower borehole assembly that could include a drilling bit, not shown in FIG. 8, that will be initially lowered by a drilling platform, not shown in FIG. 8, into the wellbore formation 85. The high flow rate and high pressure drilling fluid 83A that is able to flow freely into the lower sub-assembly lower flat face inner chamfered edge hole 4 of the lower sub-assembly 2 could then flow into the section of the lower borehole assembly that could include a drilling bit, not shown in FIG. 8, so that the high flow rate and high pressure drilling fluid 83A keeps the drilling bit, not shown in FIG. 8, well lubricated for example.
[0235] When the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 82, as shown in FIG. 8, is lowered down the wellbore formation 85 to a pre-determined depth controlled by the operator of the drilling platform, not shown in FIG. 8, the operator of the drilling fluid pump on the drilling platform, not shown in FIG. 8, can at any time remotely operate a change in the mode-of-operation of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 82, as shown in FIG. 8, from the through-flow remotely operated mode-of-operation of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 82 shown in FIG. 8, to the intermediary remotely operated mode-of-operation of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 86 shown in FIG. 9. This may be required when the operator of the drilling platform, not shown in FIG. 8, wants to transition the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 82 shown in FIG. 8, from having the high flow rate and high pressure drilling fluid 83A flowing into the lower sub-assembly lower flat face inner chamfered edge hole 4, as shown in FIG. 8, to keep the drilling bit, not shown in FIG. 8, well lubricated for example, to being used for other useful applications.
[0236] FIG. 9 shows the cross-sectional cutaway side view of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 86 operating in the intermediary remotely operated mode-of-operation whilst operating vertically in a wellbore formation 85 and being supplied with low flow rate and low pressure drilling fluid 83B.
[0237] The intermediary remotely operated mode-of-operation of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 86, as shown in FIG. 9, can be accomplished by momentarily either switching off the drilling fluid pump or decreasing the drilling fluid pump flow rate and pressure, not shown in FIG. 9, to produce low flow rate and low pressure drilling fluid 83B, as shown in FIG. 9, that is below a pre-determined drilling fluid flow rate and pressure that will not exceed the compression spring compression force characteristics including the spring force constant of the compression spring 32, and FIG. 9 shows the resultant effect on the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 86.
[0238] The lower sub-assembly tapered outer threaded section 5 of the lower sub-assembly 2, as shown in FIG. 2, of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 86, as shown in FIG. 9, will need to be interconnected to a lower borehole assembly tapered inner threaded section, not shown in FIG. 9. The lower borehole assembly tapered inner threaded section, not shown in FIG. 9, could be a section of the lower borehole assembly that could include a drilling bit, not shown in FIG. 9, that will be initially lowered by a drilling platform, not shown in FIG. 9, into the wellbore formation 85.
[0239] The upper sub-assembly tapered inner threaded section 79 of the upper sub-assembly 66, as shown in FIG. 7, of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 86, as shown in FIG. 9, will need to be interconnected to an upper borehole assembly tapered inner threaded section, not shown in FIG. 9. The upper borehole assembly tapered inner threaded section, not shown in FIG. 9, could be a section of the upper borehole assembly that could include coiled tubing, not shown in FIG. 9, that will be uncoiled and lowered by a drilling platform, not shown in FIG. 9, into the wellbore formation 85.
[0240] The drilling fluid pump on the drilling platform, not shown in FIG. 9, will pump low flow rate and low pressure drilling fluid 83B into the section of the upper borehole assembly that could include coiled tubing, not shown in FIG. 9, that will be uncoiled and lowered by a drilling platform, not shown in FIG. 9, into the wellbore formation 85. The low flow rate and low pressure drilling fluid 83B will then flow into the interconnected upper-assembly 66 of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 86. FIG. 9 shows the low flow rate and low pressure drilling fluid 83B then flowing through the upper sub-assembly lower hole 68 and through the interconnected upper sub-assembly lower flat face countersunk hole 67B. The low flow rate and low pressure drilling fluid 83B then flows onto and presses against the cycle valve upper flat face 58 of the cycle valve 53A that is inserted inside the two-part cycle valve sleeve 33A.
[0241] FIG. 9, FIG. 6B and FIG. 5B shows the cycle valve 53B is inserted longitudinally inside the two-part cycle valve sleeve 33A, as shown in FIG. 3A. The cycle valve 53B is shown in FIG. 9 to have been longitudinally displaced upwards along the centre-line axis, from the cycle valve 53A position shown in FIG. 6A and FIG. 8, along the centre-line axis and which initially results in the four cycle valve guide pins 59A, 60A, 61A, 62A to slide along the two-part cycle valve sleeve lower half short flat-sided teeth 38A, 38C, 38E, 38G, respectively. This occurs as the low flow rate and low pressure drilling fluid 83B, as shown in FIG. 9, that flows onto and presses against the cycle valve upper flat face 58 of the cycle valve 53B that is inserted inside the two-part cycle valve sleeve 33A, as shown in FIG. 6B and FIG. 9, is below a pre-determined drilling fluid flow rate and pressure that will not exceed the compression spring compression force characteristics including the spring force constant of the compression spring 32. This causes the compression spring 32 to expand and exert a longitudinal force along the centre-line axis of the cycle valve 53B. The resulting expansion of the compression spring 32, as shown in FIG. 9, results in the compression spring centralising cap 31E that is located inside the cycle valve lower flat face central hole 56B and is pressed against the cycle valve lower flat face central hole flat face 56C, to be longitudinally displaced along the centre-line axis with the cycle valve 53B, and away from the compression spring centralising cap 31A, that is inserted into the lower sub-assembly lower channel flat face central hole 29B and which presses against the lower sub-assembly lower channel flat face central hole flat face 29C, as shown in FIG. 9.
[0242] The four cycle valve guide pins 59A, 60A, 61A, 62A are constrained to travel within the two-part cycle valve sleeve separation gap 52 between the two-part cycle valve sleeve lower half upper patterned face 34B and the two-part cycle valve sleeve upper half lower patterned face 51B, as shown in FIG. 4. In-effect, the two-part cycle valve sleeve separation gap 52 acts as a patterned cam groove in which the four cycle valve guide pins 59A, 60A, 61A, 62A are constrained to travel uni-directionally within when the cycle valve 53B has a longitudinal force applied to it by the expanding compression spring 32, that results in the cycle valve 53B to be longitudinally displaced and rotated 22.5° in an uni-directional clock-wise direction about the centre-line axis of and inside the two-part cycle valve sleeve 33A. As the cycle valve 53B continues to have a longitudinal force applied to it by the expanding compression spring 32 along the centre-line axis, this results in the four cycle valve guide pins 59A, 60A, 61A, 62A to press against and then slide along the two-part cycle valve sleeve upper half long diagonal flat-sided teeth 42A, 42C, 42E, 42G, respectively, and towards the two-part cycle valve sleeve upper half curved notches 43A, 43C, 43E, 43G, respectively. The sliding action of the four cycle valve guide pins 59A, 60A, 61A, 62A along the two-part cycle valve sleeve upper half long diagonal flat-sided teeth 42A, 42C, 42E, 42G, respectively, results in the uni-directional 22.5° rotational clock-wise motion of the interconnected cycle valve 53B about the centre-line axis and from the horizontal and vertical axes, as shown in FIG. 5B, until the four cycle valve guide pins 59A, 60A, 61A, 62A are stopped by and are pressed against the two-part cycle valve sleeve upper half curved notches 43A, 43C, 43E, 43G, respectively, as shown in FIG. 6B.
[0243] The cycle valve 53B shown in FIG. 9, is now longitudinally displaced along the centre-line axis so that the cycle valve lower flat face 55 is longitudinally off-set to the two-part cycle valve sleeve lower half lower flat face 34A, and the cycle valve upper flat face 58 is shown to be resting and pressed against the upper sub-assembly lower flat face 67A. The cycle valve 53B and its four cycle valve guide pins 59A, 60A, 61A, 62A, and its four cycle valve guide pin holes 63A, 63B, 63C, 63D, and its four cycle valve truncated cone stoppers 54A, 54B, and 54C, 54D, and 54E, 54F, and 54G, 54H, and its four cycle valve through holes 64A, 64C, 64E, 64G, and its interconnected cycle valve upper flat face countersunk holes 64B, 64D, 64F, 64H, respectively, as shown in FIG. 5B and FIG. 6B and FIG. 9, have been rotationally orientated 22.5° clockwise about the centre-line axis and from the horizontal and vertical axes, from the cycle valve 53A and its four cycle valve guide pins 59A, 60A, 61A, 62A, and its four cycle valve guide pin holes 63A, 63B, 63C, 63D, and its four cycle valve truncated cone stoppers 54A, 54B, and 54C, 54D, and 54E, 54F, and 54G, 54H and its four cycle valve through holes 64A, 64C, 64E, 64G and its interconnected cycle valve upper flat face countersunk holes 64B, 64D, 64F, 64H, respectively, as shown in FIG. 5A and FIG. 6A and FIG. 8.
[0244] The low flow rate and low pressure drilling fluid 83B is able to flow freely through the cycle valve upper flat face countersunk holes 64B, 64D, 64F, 64H and the interconnected four cycle valve through holes 64A, 64C, 64E, 64G, as shown in FIG. 6B and FIG. 9. The low flow rate and low pressure drilling fluid 83B is also able to flow freely through the lower sub-assembly lower channel flat face countersunk holes 17A, 17B, 17C, 17D, and the interconnected to the lower sub-assembly lower channel holes 16A, 16B, 16C, 16D, respectively, and the interconnected lower sub-assembly inner holes 15A, 15B, 15C, 15D, respectively, and the interconnected lower sub-assembly threaded nozzles 14A, 14B, 14C, 14D. The low flow rate and low pressure drilling fluid 83B is shown in FIG. 9 to be radially sprayed at low flow rate and low pressure out of the lower sub-assembly threaded nozzles 14A, 14B, 14C, 14D and into the annulus 84.
[0245] It should be noted that the size of the arrows in FIG. 9 representing the low flow rate and low pressure drilling fluid 83B are smaller in scale and are less numerous than the size and number of the arrows in FIG. 8 representing the high flow rate and high pressure drilling fluid 83A, in order to graphically represent the difference between the low flow rate and low pressure drilling fluid 83B and the high flow rate and high pressure drilling fluid 83A.
[0246] FIG. 9 also shows that the low flow rate and low pressure drilling fluid 83B is also able to flow freely through the in-line lower sub-assembly lower channel flat face countersunk holes 28B, 28D, 28F, 28H on the lower sub-assembly lower channel flat face 30 of the lower sub-assembly 2. The low flow rate and low pressure drilling fluid 83B is then able to flow freely into the interconnected lower sub-assembly lower channel holes 28A, 28C, 28E, 28G, respectively, and into the lower sub-assembly lower flat face inner chamfered edge hole 4 of the lower sub-assembly 2.
[0247] The lower sub-assembly tapered outer threaded section 5 of the lower sub-assembly 2, as shown in FIG. 2 and FIG. 9, of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 86, as shown in FIG. 9, will need to be interconnected to a lower borehole assembly tapered inner threaded section, not shown in FIG. 9. The lower borehole assembly tapered inner threaded section, not shown in FIG. 9, could be a section of the lower borehole assembly that could include a drilling bit, not shown in FIG. 9, that will be initially lowered by a drilling platform, not shown in FIG. 9, into the wellbore formation 85. The low flow rate and low pressure drilling fluid 83B that is able to flow freely into the lower sub-assembly lower flat face inner chamfered edge hole 4 of the lower sub-assembly 2 could then flow into the section of the lower borehole assembly that could include a drilling bit, not shown in FIG. 9, so that the low flow rate and low pressure drilling fluid 83B keeps the drilling bit, not shown in FIG. 9, lubricated, for example.
[0248] The circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 86 shown in FIG. 9, could be described as being an intermediary remotely operated mode-of-operation of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1 shown in FIG. 1, where the low flow rate and low pressure drilling fluid 83B, as shown in FIG. 9, is below a pre-determined drilling fluid flow rate and pressure that will not exceed the compression spring compression force characteristics including the spring force constant of the compression spring 32, and FIG. 9 shows the resultant effect on the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 86.
[0249] FIG. 10 shows the cross-sectional cutaway side view of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 87 operating in the circulatory remotely operated mode-of-operation whilst operating vertically in a wellbore formation 85 and being supplied with high flow rate and high pressure drilling fluid 83C.
[0250] When the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 87, as shown in FIG. 10, is lowered down the wellbore formation 85 to a pre-determined depth controlled by the operator of the drilling platform, the operator of the drilling fluid pump on the drilling platform, not shown in FIG. 10, can at any time remotely operate and change the mode-of-operation of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1, as shown in FIG. 1, from the intermediary remotely operated mode-of-operation of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 86, as shown in FIG. 9, to the circulatory remotely operated mode-of-operation of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 87, as shown in FIG. 10. The circulatory remotely operated mode-of-operation of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device, as shown in FIG. 10, can be accomplished when the drill fluid pump is switched back on or the drilling fluid pump flow rate and pressure are increased again, not shown in FIG. 10, to produce high flow rate and high pressure drilling fluid 83C that is above a pre-determined drilling fluid flow rate and pressure that will exceed the compression spring compression force characteristics including the spring force constant of the compression spring 32. FIG. 10 shows the resultant circulatory remotely operated mode-of-operation of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 87.
[0251] The lower sub-assembly tapered outer threaded section 5 of the lower sub-assembly 2, as shown in FIG. 2, of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 87, as shown in FIG. 10, will need to be interconnected to a lower borehole assembly tapered inner threaded section, not shown in FIG. 10.
[0252] The lower borehole assembly tapered inner threaded section, not shown in FIG. 10, could be a section of the lower borehole assembly that could include a drilling bit, not shown in FIG. 10, that will be initially lowered by a drilling platform, not shown in FIG. 10, into the wellbore formation 85.
[0253] The upper sub-assembly tapered inner threaded section 79 of the upper sub-assembly 66, as shown in FIG. 7, of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 87, as shown in FIG. 10, will need to be interconnected to an upper borehole assembly tapered inner threaded section, not shown in FIG. 10. The upper borehole assembly tapered inner threaded section, not shown in FIG. 10, could be a section of the upper borehole assembly that could include coiled tubing, not shown in FIG. 10, that will be uncoiled and lowered by a drilling platform, not shown in FIG. 10, into the wellbore formation 85.
[0254] The drilling fluid pump on the drilling platform, not shown in FIG. 10, will pump high flow rate and high pressure drilling fluid 83C into the section of the upper borehole assembly that could include coiled tubing, not shown in FIG. 10, that will be uncoiled and lowered by a drilling platform, not shown in FIG. 10, into the wellbore formation 85. The high flow rate and high pressure drilling fluid 83C will then flow into the interconnected upper-assembly 66 of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 87, as shown in FIG. 10.
[0255] FIG. 10 shows the high flow rate and high pressure drilling fluid 83C flowing through the upper sub-assembly lower hole 68 and through the interconnected upper sub-assembly lower flat face countersunk hole 67B. The high flow rate and high pressure drilling fluid 83C then flows onto and presses against the cycle valve upper flat face 58 of the cycle valve 53C that is inserted inside the two-part cycle valve sleeve 33A.
[0256] FIG. 10, FIG. 6C and FIG. 5C shows the cycle valve 53C is inserted longitudinally inside the two-part cycle valve sleeve 33A, as shown in FIG. 3A. The cycle valve 53C is shown in FIG. 10 to have been longitudinally displaced downwards along the centre-line axis, from the cycle valve 53B position shown in FIG. 6B and FIG. 9, along the centre-line axis and which initially results in the four cycle valve guide pins 59A, 60A, 61A, 62A to initially slide along the two-part cycle valve sleeve upper half short flat-sided teeth 44A, 44C, 44E, 44G, respectively. This occurs as the high flow rate and high pressure drilling fluid 83C, as shown in FIG. 10, that flows onto and presses against the cycle valve upper flat face 58 of the cycle valve 53C that is inserted inside the two-part cycle valve sleeve 33A, as shown in FIG. 6C and FIG. 10, exceeds a pre-determined drilling fluid flow rate and pressure that will exceed the compression spring compression force characteristics including the spring force constant of the compression spring 32. This results in the compression of the compression spring 32, as shown in FIG. 10, as the compression spring centralising cap 31E that is located inside the cycle valve lower flat face central hole 56B and is pressed against the cycle valve lower flat face central hole flat face 56C, has been longitudinally displaced along the centre-line axis with the cycle valve 53C, towards the compression spring centralising cap 31A, that is inserted into the lower sub-assembly lower channel flat face central hole 29B and which presses against the lower sub-assembly lower channel flat face central hole flat face 29C, as shown in FIG. 10.
[0257] The four cycle valve guide pins 59A, 60A, 61A, 62A are constrained to travel within the two-part cycle valve sleeve separation gap 52 between the two-part cycle valve sleeve lower half upper patterned face 34B and the two-part cycle valve sleeve upper half lower patterned face 51B, as shown in FIG. 4. In-effect, the two-part cycle valve sleeve separation gap 52 acts as a patterned cam groove in which the four cycle valve guide pins 59A, 60A, 61A, 62A are constrained to travel uni-directionally within when the cycle valve 53C has a longitudinal force applied to it by the high flow rate and high pressure drilling fluid 83C, that results in the cycle valve 53C to be longitudinally displaced and rotated 22.5° in an uni-directional clock-wise direction about the centre-line axis of and inside the two-part cycle valve sleeve 33A.
[0258] As the cycle valve 53C continues to be longitudinally displaced downwards by the longitudinal force applied to it by the high flow rate and high pressure drilling fluid 83C, as shown in FIG. 10, along the centre-line axis, this results in the four cycle valve guide pins 59A, 60A, 61A, 62A to press against and then slide along the two-part cycle valve sleeve lower half long diagonal flat-sided teeth 41A, 41C, 41E, 41G, respectively, and towards the two-part cycle valve sleeve lower half curved notches 37B, 37D, 37F, 37H, respectively. The sliding action of the four cycle valve guide pins 59A, 60A, 61A, 62A along the two-part cycle valve sleeve lower half long diagonal flat-sided teeth 41A, 41C, 41E, 41G, respectively, results in the uni-directional 22.5° rotational clock-wise motion of the interconnected cycle valve 53C about the centre-line axis and from the horizontal and vertical axes, as shown in FIG. 5C, until the four cycle valve guide pins 59A, 60A, 61A, 62A are stopped by and are pressed against the two-part cycle valve sleeve lower half curved notches 37B, 37D, 37F, 37H, respectively, as shown in FIG. 6C and FIG. 10. It should be noted that the cycle valve 53C is longitudinally displaced downwards along the centre-line axis so that the cycle valve lower flat face 55 is in-line with the two-part cycle valve sleeve lower half lower flat face 34A. The cycle valve 53C shown in FIG. 10 is therefore in the same longitudinal position along the centre-line axis inside the two-part cycle valve sleeve 33A, as the cycle valve 53A shown in FIG. 8.
[0259] However, the cycle valve 53C and its four cycle valve guide pins 59A, 60A, 61A, 62A, and its four cycle valve guide pin holes 63A, 63B, 63C, 63D, and its four cycle valve truncated cone stoppers 54A, 54B, and 54C, 54D, and 54E, 54F, and 54G, 54H, and its four cycle valve through holes 64A, 64C, 64E, 64G, and its interconnected cycle valve upper flat face countersunk holes 64B, 64D, 64F, 64H, respectively, as shown in FIG. 5C and FIG. 6C and FIG. 10, are rotationally orientated 45° clockwise about the centre-line axis and from the horizontal and vertical axes, from the cycle valve 53A and its four cycle valve guide pins 59A, 60A, 61A, 62A, and its four cycle valve guide pin holes 63A, 63B, 63C, 63D, and its four cycle valve truncated cone stoppers 54A, 54B, and 54C, 54D, and 54E, 54F, and 54G, 54H, and its four cycle valve through holes 64A, 64C, 64E, 64G, and its interconnected cycle valve upper flat face countersunk holes 64B, 64D, 64F, 64H, respectively, as shown in FIG. 5A and FIG. 6A and FIG. 8.
[0260] FIG. 5C shows that the four cycle valve truncated cone stoppers 54A, 54B, and 54C, 54D, and 54E, 54F, and 54G, 54H, are extensions located on the cycle valve lower flat face 55. FIG. 6C shows that the four cycle valve truncated cone stoppers 54A, 54B, and 54C, 54D, and 54E, 54F, and 54G, 54H are longitudinally displaced along the centre-line axis and to the left past the two-part cycle valve sleeve lower half lower flat face 34A. FIG. 10 shows that the two-part cycle valve sleeve lower half lower flat face 34A is pressed against the lower sub-assembly lower channel flat face 30. FIG. 10 also shows that the four cycle valve truncated cone stoppers 54A, 54B, and 54C, 54D, and 54E, 54F, and 54G, 54H are pressed against and are seated within the lower sub-assembly lower channel flat face countersunk holes 28B, 28D, 28F, 28H, and the interconnected lower sub-assembly lower channel holes 28A, 28C, 28E, 28G, respectively, which blocks the high flow rate and high pressure drilling fluid 83C from flowing through the lower sub-assembly lower channel flat face countersunk holes 28B, 28D, 28F, 28H, and the interconnected lower sub-assembly lower channel holes 28A, 28C, 28E, 28G, respectively. The lower sub-assembly lower channel holes 28A, 28C, 28E, 28G are interconnected to and are drilled through the lower sub-assembly lower flat face inner chamfered edge hole cone 12 and into the lower sub-assembly lower flat face inner chamfered edge hole 4, as shown in FIG. 2 and FIG. 10. This occurs as the cycle valve 53C, as shown in FIG. 5C and FIG. 10, has its four cycle valve guide pins 59A, 60A, 61A, 62A, and its four cycle valve guide pin holes 63A, 63B, 63C, 63D, and its four cycle valve truncated cone stoppers 54A, 54B, and 54C, 54D, and 54E, 54F, and 54G, 54H, are all orientated 45° about the centre-line axis and from the horizontal and vertical axes of the lower end view of the cycle valve 53C of the circulating downhole tool utilizing a variable fluid pressure regulated cycle valve device 87 shown in FIG. 10. However, the high flow rate and high pressure drilling fluid 83C is able to flow freely through the cycle valve upper flat face countersunk holes 64B, 64D, 64F, 64H and the interconnected four cycle valve through holes 64A, 64C, 64E, 64G, as the lower end view of the cycle valve 53C, as shown in FIG. 5C, shows that the four cycle valve through holes 64A, 64C, 64E, 64G and the interconnected cycle valve upper flat face countersunk holes 64B, 64D, 64F, 64H, respectively, are rotationally separated by 45° about the centre-line axis and from the horizontal and vertical axes of the lower end view of the cycle valve 53C of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 87, and to the four cycle valve guide pins 59A, 60A, 61A, 62A, and the four cycle valve guide pin holes 63A,63B, 63C, 63D, and the four cycle valve truncated cone stoppers 54A, 54B, and 54C, 54D, and 54E, 54F, and 54G, 54H. The high flow rate and high pressure drilling fluid 83C is then able to flow freely through the four cycle valve through holes 64A, 64C, 64E, 64G and into the in-line lower sub-assembly lower channel flat face countersunk holes 17A, 17B, 17C, 17D, respectively, on the lower sub-assembly lower channel flat face 30 of the lower sub-assembly 2, as shown in FIG. 10. The high flow rate and high pressure drilling fluid 83C is then able to flow freely into the interconnected lower sub-assembly lower channel holes 16A, 16B, 16C, 16D, respectively, and into the interconnected lower sub-assembly inner holes 15A, 15B, 15C, 15D, respectively, and into the interconnected lower sub-assembly threaded nozzles 14A, 14B, 14C, 14D that are releaseably and securely threaded to the lower sub-assembly tapped intermediary holes 13E, 13F, 13G, 13H, respectively.
[0261] The high flow rate and high pressure drilling fluid 83C is shown in FIG. 10 to be ejected radially from the lower sub-assembly threaded nozzles 14A, 14B, 14C, 14D that are located equidistantly and are rotationally separated by 90° about the centre-line axis to one another around the lower sub-assembly upper outer surface 11B, as shown in FIG. 2 and FIG. 10.
[0262] It should be noted that the size of the arrows in FIG. 10 representing the high flow rate and high pressure drilling fluid 83C are larger in scale and are more numerous than the size and number of the arrows in FIG. 9 representing the low flow rate and low pressure drilling fluid 83B, in order to graphically represent the difference between the high flow rate and high pressure drilling fluid 83C and the low flow rate and low pressure drilling fluid 83B.
[0263] The high flow rate and high pressure drilling fluid 83C that will be injected into the annulus 84 will have the effect of increasing the annular velocity of the annulus drilling fluid 83D, so enhancing the effective cuttings transport removal 88 from the drill bit, not shown in FIG. 10, and returning along the annulus 84 to the surface, not shown in FIG. 10.
[0264] The high flow rate and high pressure drilling fluid 83C that will be injected into the annulus 84 could also be used to effectively counter loss of circulation, which occurs when the high flow rate and high pressure drilling fluid 83C flows into the wellbore formation 85 instead of returning along the annulus 84 as annulus drilling fluid 83D to the surface, by deploying or spotting remediation the high flow rate and high pressure drilling fluid 83C known as lost-circulation material LCM into the wellbore formation 85. The high flow rate and high pressure drilling fluid 83C that will be injected into the annulus 84 could also be used for wellbore clean-up operations, as the increased annulus drilling fluid 83D flow rate could be accomplished by opening annulus drilling fluid 83D flow paths above small hole internal diameter flow restricting annular sections or large outer diameter borehole assembly string components, not shown in FIG. 10, and by bypassing smaller annular sections, not shown in FIG. 10, which beneficially would allow the maximum volume flow rate of annulus drilling fluid 83D to be directed along the annulus 84, which would boost the annulus drilling fluid 83D annular velocity for more effective wellbore clean-up above the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 87 location whilst lowering the high flow rate and high pressure drilling fluid 83C pump pressure, not shown in FIG. 10.
[0265] The high flow rate and high pressure drilling fluid 83C that will be injected into the annulus 84 could also be used for reducing equivalent circulating density (ECD) window considerations at the bottom of the wellbore formation 85, and this could be achieved by using the circulatory remotely operated mode-of-operation of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 87, as shown in FIG. 10. By having the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 87 above the lower bore hole assembly BHA, not shown in FIG. 10, the lower BHA would be by-passed which would reduce the high flow rate and high pressure drilling fluid 83C pump requirements, not shown in FIG. 10, which would beneficially increase the high flow rate and high pressure drilling fluid 83C pumps reliability and operating hours, not shown in FIG. 10.
[0266] The high flow rate and high pressure drilling fluid 83C that will be injected into the annulus 84 could also be used for blowout preventer BOP stack jetting, as the circulatory remotely operated mode-of-operation of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 87, as shown in FIG. 10, would also be beneficial by being used to hydroblast any BOP cavities or subsea wellheads by dislodging debris in the BOP stack, not shown in FIG. 10.
[0267] The high flow rate and high pressure drilling fluid 83C that will be injected into the annulus 84 could also be used during liner running, not shown in FIG. 10, where the circulatory remotely operated mode-of-operation of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 87, as shown in FIG. 10, would also be beneficial by being used with auto fill float equipment, not shown in FIG. 10, by establishing two avenues of high flow rate and high pressure drilling fluid 83C communication between the BHA pipe interior, not shown in FIG. 10, and the annulus 84, so reducing the surge pressure in the annulus 84.
[0268] The lower sub-assembly tapered outer threaded section 5 of the lower sub-assembly 2, as shown in FIG. 2, of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 82, as shown in FIG. 8, will need to be interconnected to a lower borehole assembly tapered inner threaded section, not shown in FIG. 8. The lower borehole assembly tapered inner threaded section, not shown in FIG. 8, could be a section of the lower borehole assembly that could include a drilling bit, not shown in FIG. 8, that will be initially lowered by a drilling platform, not shown in FIG. 8, into the wellbore formation 85.
[0269] When the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 82, 86, 87, as shown in FIG. 8, FIG. 9, FIG. 10, respectively, is lowered down the wellbore formation 85 to a pre-determined depth controlled by the operator of the drilling platform, not shown in FIG. 8, FIG. 9, FIG. 10, the operator of the drilling fluid pump on the drilling platform, not shown in FIG. 8, FIG. 9, FIG. 10, can at any time remotely operate a change in the mode-of-operation of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 82, 86, 87, as shown in FIG. 8, FIG. 9, FIG. 10, respectively.
[0270] The through-flow remotely operated mode-of-operation of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 82, as shown in FIG. 8, 10 can be accomplished by switching on the drilling fluid pump or increasing the drilling fluid pump flow rate and pressure, not shown in FIG. 8, to produce the high flow rate and high pressure drilling fluid 83A, that exceeds a pre-determined drilling fluid flow rate and pressure that exceeds the compression spring compression force characteristics including the spring force constant of the compression spring 32 housed within the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 82, as shown in FIG. 8.
[0271] The intermediary remotely operated mode-of-operation of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 86 shown in FIG. 9, can be accomplished by the operator by momentarily either switching off the drilling fluid pump or decreasing the drilling fluid pump flow rate and pressure, not shown in FIG. 9, to produce low flow rate and low pressure drilling fluid 83B, that does not exceed a pre-determined drilling fluid flow rate and pressure that does not exceeds the compression spring compression force characteristics including the spring force constant of the compression spring 32 housed within the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 86, as shown in FIG. 9.
[0272] The circulatory remotely operated mode-of-operation of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 87, as shown in FIG. 10, can be accomplished by switching on again the drilling fluid pump or increasing the drilling fluid pump flow rate and pressure, not shown in FIG. 10, to produce the high flow rate and high pressure drilling fluid 83C, that exceeds a pre-determined drilling fluid flow rate and pressure that exceeds the compression spring compression force characteristics including the spring force constant of the compression spring 32 housed within the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 87, as shown in FIG. 10.
[0273] The bi-directional longitudinal movement and uni-directional 22.5° rotational clock-wise cyclical step movement of the cycle valve 53A, 53B, 53C along the centre-line axis inside the two-part cycle valve sleeve 33A, as shown in FIG. 6A, 6B, 6C, respectively, when a bi-directional longitudinal force produced by either the high flow rate and high pressure drilling fluid 83A, as shown in FIG. 8, or by either the expanding compression spring 32, as shown in FIG. 9, or by either the high flow rate and high pressure drilling fluid 83C, as shown in FIG. 10, is applied along the centre-line axis of the cycle valve 53A, 53B, 53C, as described in FIG. 8, FIG. 9 and FIG. 10, respectively, is designed to be repeatable for many thousands of cyclical movements of the cycle valve 53A, 53B, 53C over the life-time of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 82, 86, 87 shown in FIG. 8, FIG. 9, FIG. 10, respectively.
[0274] The cyclical movements of the cycle valve 53A, 53B, 53C along the centre-line axis inside the two-part cycle valve sleeve 33A, as shown in FIG. 6A, 6B, 6C, respectively, will occur due to the eight curved notches and eight three-flat-sided teeth pattern 42A, 43A, 44A, 45A, 46A, 42B, 43B, 44B, 45B, 46B, 42C, 43C, 44C, 45C, 46C, 42D, 43D, 44D, 45D, 46D, 42E, 43E, 44E, 45E, 46E, 42F, 43F, 44F, 45F, 46F, 42G, 43G, 44G, 45G, 46G, 42H, 43H, 44H, 45H, 46H on the two-part cycle valve sleeve upper half lower patterned face 51B, which are the mirror-image of and are circumferentially rotationally clock-wise off-set by 22.5° to the elongated circumferential side view of the eight curved notches and eight three-flat-sided teeth pattern 37A, 38A, 39A, 40A, 41A, 37B, 38B, 39B, 40B, 41B, 37C, 38C, 39C, 40C, 41C, 37D, 38D, 39D, 40D, 41D, 37E, 38E, 39E, 40E, 41E, 37F, 38F, 39F, 40F, 41F, 37G, 38G, 39G, 40G, 41G, 37H, 38H, 39H, 40H, 41H on the two-part cycle valve sleeve lower half upper patterned face 34B, as shown in FIG. 4. The four cycle valve guide pins 59A, 60A, 61A, 62A are constrained to travel within the two-part cycle valve sleeve separation gap 52 between the two-part cycle valve sleeve lower half upper patterned face 34B and the two-part cycle valve sleeve upper half lower patterned face 51B, as shown in FIG. 4. In-effect, the two-part cycle valve sleeve separation gap 52 acts as a patterned cam groove in which the four cycle valve guide pins 59A, 60A, 61A, 62A are constrained to travel uni-directionally within, when a bi-directional longitudinal force produced by either the high flow rate and high pressure drilling fluid 83A, as shown in FIG. 8, or by either the expanding compression spring 32, as shown in FIG. 9, or by either the high flow rate and high pressure drilling fluid 83C, as shown in FIG. 10, is applied along the along the centre-line axis of the cycle valve 53A, 53B, 53C, as described in FIG. 8, FIG. 9 and FIG. 10, respectively. This results in the cycle valve 53A, 53B, 53C to be longitudinally displaced and rotated 22.5° in cyclical steps in a uni-directional clock-wise direction about the centre-line axis of and inside the two-part cycle valve sleeve 33A, as shown in FIG. 6A, FIG. 8 and FIG. 6B, FIG. 9 and FIG. 6C, FIG. 10, respectively.
[0275] As an example, the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1, shown in FIG. 1, has an estimated length L1=11.500 inches and has an estimated outer diameter OD1=2.125 inches.
[0276] The lower sub-assembly 2, shown in FIG. 2, of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1, shown in FIG. 1, has an estimated length of L2=8.000 inches, and could be manufactured from 17-4 PH stainless steel.
[0277] The upper assembly 66, shown in FIG. 7, of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1, shown in FIG. 1, has an estimated length L3=5.000 inches, and could be manufactured from 17-4 PH stainless steel.
[0278] The two-part cycle valve sleeve 33A, shown in FIG. 3A and FIG. 3B, of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1, shown in FIG. 1, has an estimated outer diameter OD2=1.495 inches, and has an estimated inner diameter ID1=1.380 inches, and has an estimated height H1=1.640 inches, and has an estimated length L4=1.375 inches, and an estimated stepped length SL1=1.000 inches, and could be manufactured from alloy bronze CA104.
[0279] The two-part cycle valve sleeve 33A, shown in FIG. 3A and FIG. 4, of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1, shown in FIG. 1, has a two-part cycle valve sleeve separation gap 52 between the two-part cycle valve sleeve lower half upper patterned face 34B and the two-part cycle valve sleeve upper half lower patterned face 51B, that has an estimated patterned width P1=0.504 inches and an estimated 22.5° cyclical step pattern length PL=0.270 inches, and has an outer circumference OC of the two-part cycle valve sleeve lower half outer surface 35A, equal to sixteen times the cyclical step length, OC=PL1×16=0.270 inches×16=4.320 inches.
[0280] The cycle valve 53A, 53B, 53C of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1, shown in FIG. 5A, FIG. 5B, FIG. 5C, has an estimated outer diameter OD3=1.370 inches, and has an estimated length L5=1.000 inches, and the four cycle valve through holes 64A, 64C, 64E, 64G have an estimated internal diameter ID2=0.25 inches, and could be manufactured from 17-4 PH stainless steel.
[0281] The four cycle valve guide pins 59A, 60A, 61A, 62A of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1, shown in FIG. 6A, FIG. 6B, FIG. 6C, have an estimated length L6=0.435 inches long, and have an estimated outer diameter OD4=0.125 inches, and could be manufactured from centreless ground 17-4 PH stainless steel bar.
[0282] The compression spring centralising caps 31A, 31B of the circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1, shown in FIG. 1, have an estimated outer diameter OD5=0.490 inches, and have an estimated length L7=0.280 inches long, and could be manufactured from Polytetrafluoroethane plastic.
[0283] The lower sub-assembly tapered outer threaded section 5 and the upper sub-assembly tapered inner threaded section 79 can use American Macaroni Mining Tubing thread types.
[0284] The upper sub-assembly parallel outer threaded section 73 that is screwed into the lower sub-assembly upper flat face inner chamfered edge tapped hole 26 can use Stub ACME imperial thread types.
[0285] The circulating downhole tool utilising a variable fluid pressure regulated cycle valve device 1, shown in FIG. 1, has an estimated total mass of 4 kg.
[0286] A number of applications of the invention have been taught above and, on the basis of these, the skilled person will be aware of developments of these applications and many others applications all falling within the spirit and scope of the invention.
[0287] Whilst endeavouring in the foregoing specification to draw attention to those features of the invention believed to be of particular importance, it should be understood that the applicant claims protection in respect of any patentable feature or combination of features referred to herein, and/or shown in FIG. 1, FIG. 2, FIG. 3A, FIG. 3B, FIG. 4, FIG. 5A, FIG. 5B, FIG. 5C, FIG. 6A, FIG. 6B, FIG. 6C, FIG. 7, FIG. 8, FIG. 9 and FIG. 10 whether or not particular emphasis has been placed thereon.
[0288] It will be appreciated that embodiments of the present invention can be realised in the form of hardware, software or a combination of hardware and software. Any such software may be stored in the form of volatile or non-volatile storage such as, for example, a storage device like a ROM, whether erasable or rewritable or not, or in the form of memory such as, for example, RAM, memory chips, device or integrated circuits or on an optically or magnetically readable medium such as, for example, a CD, DVD, magnetic disk or magnetic tape. It will be appreciated that the storage devices and storage media are embodiments of machine-readable storage that are suitable for storing a program or programs that, when executed, implement embodiments of the present invention. Accordingly, embodiments provide a program comprising code for implementing a system or method as disclosed in any aspect, example, claim or embodiment of this disclosure, and a machine-readable storage storing such a program. Still further, embodiments of the present disclosure may be conveyed electronically via any medium such as a communication signal carried over a wired or wireless connection and embodiments suitably encompass the same.
[0289] All of the features disclosed in this specification (including any accompanying claims, abstract and drawings), and/or all of the steps of any method or process so disclosed, may be combined in any combination, except combinations where at least some of such features and/or steps are mutually exclusive. Each feature disclosed in this specification (including any accompanying claims, abstract and drawings), may be replaced by alternative features serving the same, equivalent or similar purpose, unless expressly stated otherwise. Thus, unless expressly stated otherwise, each feature disclosed is one example only of a generic series of equivalent or similar features.
[0290] The invention is not restricted to the details of any foregoing embodiments. The invention extends to any novel one, or any novel combination, of the features disclosed in this specification (including any accompanying claims, abstract and drawings), or to any novel one, or any novel combination, of the steps of any method or process so disclosed. The claims should not be construed to cover merely the foregoing embodiments, but also any embodiments which fall within the scope of the claims, including with equivalence.
