Prime Mover System and Methods Utilizing Balanced Flow within Bi-Directional Power Units

Abstract

Systems, methods and devices are described providing a selective hydraulic or electrically powered prime mover that is a (bi-directional power unit) PU system, including movement within a device or system used to compress and/or expand a fluid and provide fluid movement within the same device or system. The use of a (hydraulic power unit) HPU is involved and comprises at least a pump or other hydraulic fluid moving device often referred to as a prime mover, one or more first set of selective control valves delivering pressurized fluid to the device(s), and one or more second set of selective control valves returning unpressurized fluid from the device(s), a reservoir comprising a compensator tank, a port allowing for operation at ambient pressure, and a pressure measuring device measuring ambient pressure allowing for unbalanced flow to and from the mechanical (user) device as well as thermal expansion or compression.

Claims

1. A prime mover apparatus and system for actuating and moving one or more devices in either a single or bi-directional direction using at least one hydraulic power unit(s) comprising; one or more pumps, said pumps having at least one inlet and at least one outlet port maintaining pressure to pump fluid in either a clockwise or counterclockwise direction into and out of a pipeline such that said fluid enters and exits said pumps from either a designated clockwise (CW) or counterclockwise (CCW) outlet port thereby creating a clockwise or counterclockwise flow path utilizing valves ensuring balanced fluid flow into and out of said pumps.

2. The prime mover apparatus and system of claim 1, wherein said valves allow for fluid flow into and out of at least one reservoir.

3. The prime mover apparatus and system of claim 1, wherein said at least one reservoir is vented, sealed, pressure compensated, preloaded and/or expandable.

4. The prime mover apparatus and system of claim 1, wherein said valve(s) open and close ensuring balanced fluid flow along said flow path with force and direction required to move said moving device(s) in a precise and controlled fashion determined by a user.

5. The prime mover apparatus and system of claim 1, wherein fluid is delivered to at least one port within said moving device(s) and fluid along said flow path from said moving device(s) is blocked, redirected, or continues to flow into one or more additional valves, said additional valves containing components that control fluid flow returning from said moving device(s) back into said pump, thereby completing said flow path and accomplishing an ability to control intermittent or continuous movement of said moving devices.

6. The apparatus and system of claim 1, wherein said apparatus and system is an electrical power unit(s) apparatus for actuating and moving one or more devices in either a single or bi-directional direction wherein said hydraulic and/or electric power units are selected from the group consisting of pumps, motors, compressors, engines, turbines and inverters and wherein said pumps can be positive displacement pumps.

7. The apparatus and system of claim 1, wherein fluid flow along said flow path continues flowing into and out of said pumps thereby keeping one or more motor seals and associated ports filled with fluid, thereby reducing or eliminating hydraulic lock and cavitation.

8. The apparatus and system of claim 1, wherein said system also includes a pressure compensator tank that is operationally connected to a pump inlet port of said pump through an optional fluid flow filter and wherein said compensator tank is a portion of a variable fluid reservoir.

9. The apparatus and system of claim 1, wherein said one or more pumps are a motor.

10. The apparatus and system of claim 1, wherein said fluid reservoir includes at least one compensator tank and a port to ambient pressure and an optional reservoir pressure measuring device that measures ambient pressure and ensures the ability for said system to operate even in the presence of unbalanced flow to and from said moving device(s) and allows for thermal expansion or compression within said system.

11. The apparatus and system of claim 1, wherein said system is a closed system in that said pipeline is completely closed and has no open ports to the atmosphere.

12. The apparatus and system of claim 1, wherein said system is an open system in that said pipeline has at least one port that is opened to the atmosphere.

13. The apparatus and system of claim 1, wherein said user utilizes a controller to increase volume, change direction, and/or increase static or dynamic pressure within said fluid along said flowpath.

14. The apparatus and system of claim 3, wherein fluid within said fluid reservoir is controlled by a controller.

15. The apparatus and system of claim 1, wherein fluid reaches an upper bi-directional port of said moving device(s) and is delivered to said moving device(s) and returns from said moving device(s) into a lower bi-directional port.

16. The apparatus and system of claim 1, wherein at least one valve is a check valve and said check valve has two ports.

17. The apparatus and system of claim 1, wherein said system contains at least one set of pilot operated check valves and wherein said pilot operated check valves have at least three ports.

18. The apparatus and system of claim 1, wherein said system contains at least two sets of pilot operated check valves.

19. The apparatus and system of claim 1, wherein one or more valves is a detented shuttle valve with at least three ports.

20. The apparatus and system of claim 1, wherein one or more valves is an inverted shuttle valve with at least three ports.

21. The apparatus and system of claim 1, wherein said pipeline has at least one fluid flow filter.

22. The apparatus and system of claim 1, wherein said pipeline has at least one pressure measuring device.

23. The apparatus and system of claim 1, wherein said one or more devices are selected from the group consisting of; mechanical devices, electro-mechanical devices and electro-hydraulic devices.

24. The apparatus and system of claim 1, wherein said one or more devices are valves, gate valves, ball valves, seat valves, flapper valves, rotary valves, sleeve valves, packers, gears, sub-assemblies, hydraulic cylinders, hydraulic rotary actuators, bladders, accumulators, and reservoirs.

25. The apparatus and system of claim 1, wherein valves are selected from the group consisting of: shuttle valves, inverted shuttle valves, inverse shuttle valves, detented shuttle valves, inverted detented shuttle valves, check valves, pilot check valves, solenoid valves, servo valves, ball valves, and gate valves.

26. The apparatus and system of claim 1, wherein said valves are provided in parallel, in series, or in any combination of parallel and series throughout said system so that said system is operational in that fluid can travel in either a unidirectional and/or bi-directional flow path through said system and so that fluid powers devices that operate in either a singular or bi-directional fashion.

27. The apparatus and system of claim 1, wherein said hydraulic power unit (HPU) moves a prime mover by using energy to move fluid in a flow path.

28. The apparatus and system of claim 1, wherein said hydraulic power unit (HPU) extracts energy from a flow path to an external energy sink.

29. The prime mover apparatus and system of claim 1, wherein said prime mover apparatus is a flow measuring device.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0059] FIGS. 1A and 1E are schematic illustrations of a CW/CCW fluid-based pumping only power unit with shuttle valves, illustrating a valving system according to one or more embodiments.

[0060] FIGS. 1B-1D provide detailed enlarged portions of the valve components of FIGS. 1A and 1E.

[0061] FIGS. 2A and 2C are schematic illustrations of a CW/CCW fluid-based pumping and generation power unit with shuttle valves connected to a balanced flow device, illustrating a valving system according to one or more embodiments.

[0062] FIG. 2B provides detailed enlarged portions of the valve components of FIGS. 2A and 2C.

[0063] FIGS. 3A-3B are schematic illustrations of a CW/CCW fluid-based pumping and generation power unit with shuttle valves connected to an unbalanced flow device, illustrating a valving system according to one or more embodiments.

[0064] FIG. 4 is a schematic illustration of a CW/CCW fluid-based power unit, illustrating an accumulator included in a valving system according to one or more embodiments.

[0065] FIGS. 5A and 5C are schematic illustrations of a CW/CCW fluid-based power unit with return flow pilot check valves, illustrating a valving system according to one or more embodiments.

[0066] FIGS. 5B and 5D provide detailed enlarged portions of the valve components of FIGS. 5A and 5C.

[0067] FIGS. 6A, 6C and 6D are schematic illustrations of a CW/CCW fluid-based power unit with pressure blocking pilot check valves, illustrating a valving system according to one or more embodiments.

[0068] FIG. 6B provides detailed enlarged portions of the valve components of FIGS. 6A, 6C and 6D.

[0069] FIGS. 7A and 7B are schematic illustrations of a CW/CCW fluid-based power unit with pressure blocking pilot check valves connected to a single ended flow device, illustrating a valving system according to one or more embodiments.

[0070] FIG. 7C is a schematic illustration of a static fluid-based power unit, illustrating a valving system according to one or more embodiments.

DETAILED DESCRIPTION

[0071] In some embodiments of the present disclosure, an actuator, such as a valve can include one or more pump systems, such as for example, one or more hydraulic pumps that can be used to move one or more fluids within the actuators. U.S. Provisional App. No. 61/216,942, to Ingersoll, et al., filed May 22, 2009, entitled Compressor and/or Expander Device, and U.S. patent application Ser. Nos. 12/785,086, 12/785,093 and 12/785,100, each filed May 21, 2010 and entitled Compressor and/or Expander Device (collectively referred to herein as the the Compressor and/or Expander Device applications), the disclosures of which are hereby incorporated herein by reference, in their entireties, describe various energy compression and/or expansion systems in which the systems and methods described herein can be employed.

[0072] The hydraulic actuator can be coupleable to a hydraulic pump, which can have efficient operating ranges that can vary as a function of, for example, flow rate and pressure, among other parameters. Systems and methods of operating the hydraulic pumps/motors to allow them to function at an optimal efficiency throughout the stroke or cycle of the gas compression and/or expansion system are described in U.S. patent application Ser. No. 12/977,724 to Ingersoll, et al., filed Dec. 23, 2010, entitled Systems and Methods for Optimizing Efficiency of a Hydraulically Actuated System, (the '724 application) the disclosure of which is incorporated herein by reference in its entirety as well as U.S. Pat. No. 8,522,538 entitled Systems and methods for compressing and/or expanding a gas utilizing a bi-directional piston and hydraulic actuator.

[0073] Most specifically, the present disclosure includes the embodiments as shown in FIGS. 1-7 and described below. For all figures, the keys provided indicate high pressure flow and static lines are bolded while the low pressure flow and static lines are presented as unbolded. Arrows are used to indicate clockwise and/or counterclockwise direction(s) for the flow. This allows for unidirectional or bidirectional flow to occur as presented. Inactive lines are presented as dashed for flow or dotted for static lines. The filled dots represent areas of high pressure and static flow, the unfilled dots represent areas of low pressure and static flow, both within the piping system.

[0074] FIG. 1A is a schematic that provides an initial embodiment of the present disclosure illustrating the HPU system I (100) utilizing one or more pressure pumps that operate in CW (clockwise) or CCW (counter clockwise) rotation, to accomplish supplying high pressure fluid to a mechanical (user) device and returning low pressure fluid from the device back to at least one pump. This system is referred to as a hydraulic power unit (HPU) that powers the prime mover. The power unit (PU) could also be driven by electrical power derived from various sources including wind and solar energy.

[0075] Here the HPU system I (100) utilizes the pump (110), having a single inlet port (112), in the CW direction so that the fluid reaches the upper bi-directional port (140) and is delivered to the mechanical (user) device and returns from the mechanical (user) device into lower bi-directional port (160). Although the system described is directed to moving mechanical (user) devices, it is to be understood that the prime mover concept taught herein is also applicable to moving devices that are not mechanical.

[0076] The fluids' path in this case starts with one or more pump or pumps (110) such that the fluid exits the pump (110) from the CW outlet port (114), goes through the first CW optional fluid flow filter (120), as further detailed in FIG. 1B and CW check valve (130). The check valve is utilized to ensure that the fluid continues to flow in the proper direction. The fluid is delivered through the second optional fluid flow filter (135) to the upper bi-directional port (140). In addition, fluid is also delivered to a detented shuttle valve (150), for which an expanded (exploded) view is provided in FIG. 1C, and continues through the detented shuttle valve port A, herein port A (154) to detented shuttle valve port C, herein port C (152). The detented shuttle valve (150) is activated by the pressure on port A (154) moving the shuttle (157) from port A sealing O rings (158), located near port A (154), to port B sealing O rings (159), located near detented shuttle valve port B, herein port B (156). The detented shuttle valve (150) is retained in position by the friction of the shuttle (157) against the port B sealing O rings (159). Flow continues and is now communicated from port A (154) to port C (152) that is connected to an optional pressure measuring device (155).

[0077] In addition, flow is blocked by the shuttle (157) and port B sealing O rings (159) from exiting port B (156).

[0078] Also additionally, in FIG. 1A and provided in further detail in the expanded view shown in FIG. 1D the flow is directed to an inverted shuttle valve (170) specifically to inverted shuttle valve port D, herein port D (174) which moves the primary bar-bell shaped shuttle (177) thereby closing the upper portion inverted shuttle valve (178) and opening the lower portion inverted shuttle valve (179). This allows returning flow from lower bi-directional port (160) through optional fluid flow filter (165) to the inverted shuttle valve (170) but specifically to and through inverted shuttle valve port E, herein port E (176) thereby exiting inverted shuttle valve port F, herein port F (172). Completing the flow path within this closed system; the fluid flow continues to be flowing and utilizing pump (110) and specifically to pump inlet port (112). Note that the optional pressure compensator tank (190) is operationally connected to pump inlet port (112) through the optional fourth fluid flow filter (180). The compensator is a portion of the reservoir (191) (comprising the compensator tank (190), a port to ambient pressure (195) and an optional reservoir pressure measuring device (192) for measuring ambient pressure) that ensures the ability for a sealed (closed) system to operate even in the presence of unbalanced flow to and from the mechanical (user) device. In addition, it allows for thermal expansion or compression within the sealed (closed) system. This completes the flow path within this closed system.

[0079] FIG. 1E provides an identical schema as shown in FIG. 1A, with the exception, however, that in this case the pump or pumps (110) are rotated in a CCW fashion. The resulting fluid flow path now provides one or more hydraulically operable mechanical (user) devices (not shown) for the pressurized fluid to exit from the lower bi-directional port (160) and return as unpressurized fluid from the upper bi-directional port (140). Specifically fluid is being delivered to the lower bi-directional port (160) and taken from the upper bi-directional port (140) that controls the mechanical (user) devices (typically a rotary actuator or piston) as follows; the fluids' path in this case starts with pump or pumps (110) where the fluid exits the pump (110) from the CCW outlet port (116), goes through the first CCW optional fluid flow filter (122), as further detailed in FIG. 1B and CCW check valve (132). Fluid flows to and through the detented shuttle valve (150), moving the shuttle (157) from port B sealing O rings (159) to port A sealing O rings (158) connecting port B (156) to port C (152) and blocking port A(154).

[0080] Also additionally, the flow is directed to and through an inverted shuttle valve (170) specifically to port D (176) which moves the primary bar-bell shaped shuttle (177) thereby closing the lower portion inverted shuttle valve (179) and opening the upper portion inverted shuttle valve (178). This allows returning flow from the upper bi-directional port (140) through the second optional fluid flow filter (135) to the inverted shuttle valve (170) but specifically to and through port D (174) thereby exiting port F (172). Completing the flow path within this closed system; the flow continues to pump (110) and specifically sends the fluid to the pump inlet port (112).

[0081] FIG. 2A is a schematic that details another embodiment of the present disclosure utilizing a motor (210), where in this embodiment the prime mover is also hydraulic powered but could also be electrically powered. Using the motor or motors (210) instead of a pump with the check valve arrangement such as in FIGS. 1A and 1E allows for the system to be run in the reverse direction and thereby the motors could also be utilized as energy generators. Again the use of the system will depend on the required need(s)in many cases utilizing the system to generate energy will be required. Here, this embodiment the HPU system II (200) utilizes the motor in the CW direction so that the fluid reaches the upper bi-directional port (140) to deliver fluid to a balanced hydraulic actuator (280) such as a hydraulic cylinder with piston faces of equal surface areas. The fluid returns from the balanced hydraulic actuator (280) to the lower bi-directional port (160). The fluid path in this case, beginning at the motor or motors (210), provides for fluid exiting the motor from the CW outlet port (114) and flowing through the first CW optional fluid flow filter (120), as shown in expanded detail in FIG. 2B. The fluid is next delivered through the second optional fluid flow filter (135) to the upper bi-directional port (140). In addition the fluid is delivered to a detented shuttle valve (150) and continues through port A (154) to port C (152). The detented shuttle valve is activated by the pressure on port A (154) moving the shuttle (157) from the port A sealing O rings (158), located near port A (154), to the port B sealing O rings (159) located near port B (156). The detented shuttle valve is retained in position by the friction of the shuttle (157) against the port B sealing O rings (159). Flow continues and is now communicated from port A (154) to port C (152) which is also connected to optional pressure measuring device (155).

[0082] In addition, flow is blocked by the shuttle (157) and the port B sealing O rings (159) from exiting shuttle valve port B (156), a provided in detail in FIG. 1C.

[0083] In this instance, there are two distinct return flow paths. The first return fluid flow path returns from the balanced hydraulic actuator (280) to the lower bi-directional port (160) through the third optional fluid flow filter (165) to the motor (210), into the CCW outlet port (116) and through the first CCW optional fluid flow filter (122). It is critical here that the flow through the motor (210) must have an exactly equal flow entering the CCW outlet port (116) as is exiting the CW outlet port (114). Without this condition, the motor will begin to cavitate and operate improperly or abnormally (as opposed to operating properly or normally).

[0084] The second return flow path is enabled by the high pressure flow line connected to the inverted shuttle valve (170) specifically to port D (174) which moves the primary bar-bell shaped shuttle (177) thereby closing the upper portion inverted shuttle valve (178) and opening the lower portion inverted shuttle valve (179). This allows returning flow from the lower bi-directional port (160) through the third optional fluid flow filter (165) to the inverted shuttle valve (170) but specifically to and through port E (176) thereby exiting port F (172). Completing the flow path, the flow continues to the motor (210) and specifically to the motor seal port (112), which is a requirement for the proper operation of the motor (210). What is achieved by this second return flow path is that the fluid pressure across the seal is kept within the manufacture's specifications. Without this static pressure equalization caused by this operation of the inverted shuttle valve (170), the internal motor shaft seals (not numbered) will fail. Motor shaft seals are seals that exist around the shaft of a motor to ensure that when the shaft rotates it does not build excessive heat and allows for heat (due to mechanical friction) to be transferred through the seals to a heat transfer fluid.

[0085] Note that the optional pressure compensator tank (190) is connected to the inverted shuttle valve (170) and port F (172). The pressure compensator tank (190) is a portion of the reservoir (191) (comprising the compensator tank (190), a port to ambient pressure (195) and an optional reservoir pressure measuring device (192) measuring ambient pressure) that ensures the ability for a sealed (closed) system to operate even in the presence of unbalanced flow to and from the balanced hydraulic actuator (280). In addition, it allows for thermal expansion or compression within the sealed (closed) system. This completes the flow path within this closed system.

[0086] FIG. 2C provides the identical schema as shown for FIG. 2A, however in this case the motor or motors (210) are rotated in a CCW flow fashion. The resulting fluid flow path now provides for a balanced hydraulic actuator (280) for the pressurized fluid to exit from lower bi-directional port (160) and return as unpressurized fluid from upper bi-directional port (140). Specifically this is accomplished by fluid flowing to and through the detented shuttle valve (150) moving through the shuttle (157) from port B sealing O rings (159) to the port A sealing O rings (158) connecting port B (156) to port C (152) and blocking port A (154).

[0087] Also additionally, the flow is directed to and through an inverted shuttle valve (170) specifically to port E (176) which moves the primary bar-bell shaped shuttle (177) thereby closing the upper portion inverted shuttle valve (178) and opening the lower portion inverted shuttle valve (179). This allows returning flow from the upper bi-directional port (140) through optional second fluid flow filter (135) to the inverted shuttle valve (170) but specifically to and through port D (174) thereby exiting port F (172). Completing the flow path within this closed system; the flow continues to the motor (210) and specifically motor seal port (112).

[0088] FIG. 3A provides the same schema as shown in FIG. 2A, utilizing a motor (210) where in this embodiment the prime mover is also primarily hydraulic. Here, however, the HPU system III (300) utilizes the motor (210) in the CW direction so that the fluid reaches the upper bi-directional port (140) to deliver fluid to an unbalanced hydraulic actuator (380) (the mechanical user device) such as a hydraulic cylinder with piston faces of unequal surface areas. The fluid returning also returns by two distinct flow paths from the unbalanced hydraulic actuator (380) to the lower bi-directional port (160).

[0089] In this instance, there are also two distinct return flow paths. The first return fluid flow is identical to that of FIG. 2A, however from an unbalanced hydraulic actuator (380) to the lower bi-directional port (160) through the third optional fluid flow filter (165) to the motor (210) and specifically the CCW outlet port (116) through first CCW optional fluid flow filter (122). It is critical here that the flow through the motor (210) must have an exactly equal flow entering the CCW outlet port (116) as is exiting the CW outlet port (114). To accomplish this condition, any imbalance of flow is compensated by the second return flow path. In the second return flow path, which can be described identically to that of the description for FIG. 2A, an imbalance could be either an excess of fluid returning from the unbalanced hydraulic actuator (380) or insufficient fluid from the unbalanced hydraulic actuator (380). If there is an excess of fluid, the excess flows through inverted shuttle valve (170) into the pressure compensation tank (190). If the flow is insufficient, then flow will be directed from the compensation tank (190) to the inverted shuttle valve (170) back toward the motor (210

[0090] Note that the optional pressure compensator tank (190) is connected to the inverted shuttle valve (170) and port F (172) to ensure that the volumetric flow of fluid into and out of the hydraulic motor (210) remains the same as described above. This completes the flow path within this closed system The HPU system does not have to be a closed system. The pressure compensation tank (190) could be a reservoir that has the required size and location to operate as an energy storage mechanism where fluid from an external source could be pumped into the reservoir effectively storing energy within the reservoir. The reservoir would then be drainedas required through the HPU to generate power.

[0091] FIG. 3B provides the identical schema as for FIG. 3A, however in this case the motor or motors (210) are rotated in a CCW flow fashion. The resulting fluid flow path now provides for an unbalanced hydraulic actuator (380) for the pressurized fluid to exit from the lower bi-directional port (160) and return as unpressurized fluid from upper bi-directional port (140). Specifically, this is accomplished by fluid flowing to and through the detented shuttle valve (150) moving the shuttle (157) from port B sealing O rings (159) to port A sealing O rings (158) therefore connecting port B (156) to port C (152) and blocking port A(154). A make-up fluid flow is required to keep the fluid system equilibrated. This flow is provided as a low pressure line from the fluid reservoir (191), because out-flow from the unbalanced hydraulic actuator (380) is less than the in-flow to the unbalanced hydraulic actuator (380) when actuated in this direction.

[0092] Also additionally, the make-up fluid flow is directed from the fluid reservoir (191) to and through the fourth optional fluid filter (180)) thereby entering the inverted shuttle valve (170) specifically through port F (172) and exiting specifically to and through port D (174). Completing the flow path within this closed system; the flow continues to the motor (210) specifically entering through the CW inlet port (114).

[0093] FIG. 4 is a schematic of HPU system IV (400) which is identical to FIGS. 2A and 2C and FIGS. 3A and 3B with the addition of an accumulator (490) and reversible pressurization of the previously static line from the reservoir (191) to the junction adjacent to the second optional fluid filter (165). The primary purpose of the accumulator (490) is to store and release hydraulic energy by storing excess energy created by the motor or motors (210) and releasing the stored energy on demand. This results in a system that improves the longevity of the motor by reducing mechanical wear on the components due to lessening of the transient pressure fluctuations due to larger fluctuations between high and low flow rates and pressures. The accumulator (490) can store energy that allows intermittent operation of the motor or motors (210) as required. In addition the accumulator (490) can store energy available from the hydraulic actuator (balanced (280) or unbalanced (380)) to be utilized by the motor or motors (210) when the motor operates in a reverse direction thereby acting as a generator. If the hydraulic actuator (balanced (280) or unbalanced (380), and not shown) has intermittent loads during operation this configuration allows for utilizing the stored energy over the necessary period of time during the operation. This alleviates the need for the motor (210) to instantly use the stored energy in a system that includes both the accumulator (490) and the reservoir (191). It should be noted that energy stored in or taken from the accumulator (in any form) allows for a myriad of uses including be used as a controller or together with a controller to activate or deactivate numerous devices.

[0094] For illustration purposes the flow conditions as described in FIG. 2A are provided as an example for a balanced CW mode. Specifically, FIG. 2A is a schematic that details an embodiment that is essentially identical to FIG. 4 with the exception of the addition the accumulator (490) and reversible pressurization of the previously static line from the reservoir (191) to the junction adjacent to the second optional fluid filter (165). Here again the HPU system IV (400) utilizes the motor in the CW direction so that the fluid reaches upper bi-directional port (140) to deliver fluid to a balanced hydraulic actuator (280) such as hydraulic cylinder with piston faces of equal surface areas. The fluid returns from the balanced hydraulic actuator (280) to lower bi-directional port (160). The fluids' path in this case starting with motor or motors (210) where the fluid exits the motor from the CW port (114) goes through first CW optional fluid flow filter (120). The fluid is next delivered through the second optional fluid flow filter (135) to the upper bi-directional port (140). In addition the fluid is delivered to a detented shuttle valve (150) and continues through port A (154) to port C (152). The detented shuttle valve is activated by the pressure on port A (154) moving the shuttle (157) from port A sealing O rings (458) to port B sealing O rings (459).The detented shuttle valve (150) is retained in position by the friction of the shuttle (157) against the port B sealing O rings (159). Flow continues and is now communicated from port A (154) to port C (152) that is connected to optional pressure measuring device (155).

[0095] In addition, flow is blocked by the shuttle (157) and port B sealing O rings (159) from exiting port C (156).

[0096] In this instance, there are two distinct return flow paths. The first return fluid flow path returns from the balanced hydraulic actuator (280) to lower bi-directional port (160) through optional third fluid flow filter (165) to motor (210) and specifically CCW outlet port (116) through first CCW optional fluid flow filter (122). It is critical here that the flow through the motor (210) must have an exactly equal flow entering CCW outlet port (116) as is exiting CW outlet port (114). Without this condition, the motor (210) will begin to cavitate and operate improperly or abnormally (as opposed to operating properly or normally).

[0097] The second return flow path has flow that is directed to an inverted shuttle valve (170) specifically to port D (174) which moves the primary bar-bell shaped shuttle (177) thereby closing the upper portion inverted shuttle valve (178) and opening the lower portion inverted shuttle valve (179). This allows returning flow from the lower bi-directional port (160) through the third optional fluid flow filter (165) to the inverted shuttle valve (170) but specifically to and through port E (176) thereby exiting port F (172). Completing the flow path, the flow continues to the reservoir (191). This second return flow path is reversible depending on the direction of flow into and out of the accumulator (490). Fluid of the second return path can be directed to the motor (210) and specifically to the motor seal port (112), which is a requirement for the proper operation of the motor(s) (210). What is achieved by this second return flow path is that the fluid pressure across the seal is within the manufacture's specifications. Without this static pressure equalization caused by this operation of the inverted shuttle valve (170), the shaft seals will fail.

[0098] Note that the optional pressure compensator tank (190) is connected, through fourth optional fluid flow filter (180), to the inverted shuttle valve (170) and port F (172). The pressure compensator tank (190) is a portion of the reservoir (191) (comprising the compensator tank (190), a port to ambient pressure (195) and an optional second pressure measuring device (192) measuring ambient pressure) that ensures the ability for a sealed (closed) system to operate even in the presence of unbalanced flow to and from the balanced hydraulic actuator (280). In addition, it allows for thermal expansion or compression within the sealed (closed) system. This completes the flow path within this closed system.

[0099] In addition, there is an accumulator (490) which is connected to the detented shuttle valve (150) through port C (152) as well as to the inverted shuttle valve (170) and shuttle port F (172). The flow into the accumulator (490) allows for excess flow from the motor (210) which is not being utilized by the hydraulic actuator (balanced (280) or unbalanced (380)) flows through detented shuttle valve (150) through port A(154) exiting port C(152) and is stored in the accumulator (490). Alternatively available stored energy in the accumulator (490) is available to actuate the hydraulic actuator (balanced (280) or unbalanced (380)) as needed by flow through the detented shuttle valve (150) through port C (152) exiting port A (154). Excess energy available from the hydraulic actuator (balanced (280) or unbalanced (380)) can be sorted in the accumulator (490) by flowing through the detented shuttle valve (150) going into port A (154) and exiting port C (152). Stored energy in the accumulator (490) can be utilized to generate energy as required by the motor or motors (210) by flowing through the detented shuttle valve (150) with the flow flowing into port C (152) and exiting port A (154) to the motor (210) and in this case the CW outlet port (114). This forward and reverse flow path system is operational with or without an accumulator (490).

[0100] FIG. 5A essentially provides the same schema as FIG. 4, with the exception that the inverted shuttle valve of FIG. 4 (170) has been replaced by an upper pilot operated check valve (565) and lower pilot operated check valve (570). This valving combination provides the ability that when there is no flow through the system the pilot operated check valves (565, 570) isolate the pressure differential between the hydraulic actuator (balanced (280) or unbalanced (380), and not shown) connected to the upper bi-directional (140) and lower bi-directional port (160). This is important because pressure differentials associated with any hydraulic actuators (balanced (280) or unbalanced (380)) allow for these pilot operated check valves (565, 570) to ensure the pressure compensator tank(190) does not receive large, potentially damaging, pressure differences that may occur and migrate through the system during operation. In this manner, the pilot operated check valves (565, 570) operate as a form of safety valvesproviding protection from damaging, in this case the pressure compensator tank (190).

[0101] FIG. 5A is a schematic which is also identical to FIG. 2A and FIG. 3A with the addition of an accumulator (490). The accumulator (490) can store energy that allows intermittent operation of the motor or motors (210) as required. In addition the accumulator (490) can store energy available from the hydraulic actuator (balanced (280) or unbalanced (380), and not shown) to be utilized by the motor (210) when the motor operates in a reverse direction thereby acting as a generator. In this case no hydraulic actuator (balanced (280) or unbalanced (380)) is shown, but again there may be and often are intermittent loads during operation. This configuration allows for utilizing the stored energy over the necessary period of time during the operation. This alleviates the need for the motor to instantly use the stored energy in the system.

[0102] For illustration purposes the flow conditions are as described in FIG. 2A, FIG. 3A and FIG. 4 and is provided as an example for a CW flow. Here again the HPU system V (500) utilizes the motor (210) in the CW direction so that the fluid reaches the upper bi-directional port (140) to deliver fluid to an actuator or other user device (not shown). The fluid returns from the lower bi-directional port (160) after exiting the upper bi-directional port (140) from the user device (not shown). The fluid path in this case is as follows; starting with the fluid flowing from the motor or motors (210), exits the motor from the CW outlet port (114) and proceeds through the first optional fluid flow filter (120) in the CW direction. The fluid is next delivered through the second optional fluid flow filter (135) to the upper bi-directional port (140). In addition, the fluid is delivered to a detented shuttle valve (150) and continues through port A (154) to port C (152). The detented shuttle valve is activated by the pressure on port A (154) moving the shuttle (157) from port A sealing O rings (158), located near port A (154) to port B sealing O rings (159) located near port B (156). The detented shuttle valve (150) is retained in position by the friction of the shuttle (157) against the port B sealing O rings (159). Flow continues and is now communicated from port A (154) to port C (152) so that it is in communication with an optional pressure measuring device (155).

[0103] In addition, flow is blocked by the shuttle (157) and the port B sealing O rings (159) from exiting shuttle valve port B (156). In this case there is also an upper pilot operated check valve (570) which is in the blocked condition.

[0104] In this instance, there are two distinct return flow paths. The first return fluid flow path returns from the actuator (not shown) to the lower bi-directional port (160) through optional third fluid flow filter (165) to motor (210) and specifically the CCW outlet port (116) through first CCW optional fluid flow filter (122). It is critical here that the flow through hydraulic motor (210) must have an exactly equal flow entering the CCW outlet port (116) as is exiting the CW outlet port (114). Without this condition, the motor will begin to cavitate and operate improperly or abnormally (as opposed to operating properly or normally).

[0105] The second return flow path is enabled by the high pressure flow line connected to the lower pilot operated check valve (565), as provided in detail in FIG. 5B, specifically to lower pilot operated check valve port G, herein port G (568) which opens the lower pilot operated check valve (565) allowing bi-directional flow between lower pilot operated check valve port H, herein port H (566) and lower pilot operated check valve port I, herein port I (567). This allows returning flow from the lower bi-directional port (160) through the third optional fluid flow filter (135) to the lower pilot operated check valve (565) but specifically to and through port H (566) thereby exiting port I (567). Completing the flow path, the flow continues to the motor (210) which is a requirement for the proper operation of the motor(s) (210). What is achieved by this second return flow path is that the fluid pressure across the seal maintains the pressure so that it is within the manufacture's specifications. Without this static and dynamic pressure equalization caused by this operation of the lower and upper pilot operated check valves (565, 570) of inverted shuttle valve (170), the internal motor shaft sealswhich must be properly pressurized (not shown)will fail.

[0106] Again, there is an optional pressure compensator tank (190) that is connected to the lower pilot operated check valves (565) and port G (568). The pressure compensator tank (190) is a portion of the reservoir (191) (comprising the compensator tank (190), a port to ambient pressure (195) and a second optional pressure measuring device (192) measuring ambient pressure) that ensures the ability for a sealed (closed) system to operate even in the presence of unbalanced flow to and from the balanced hydraulic actuator (280). In addition, it allows for thermal expansion or compression within the sealed (closed) system. This completes the flow path within this closed system.

[0107] In addition, there is an accumulator (490) which is connected to the detented shuttle valve (150) through port C (152) as well as to both the lower and upper pilot operated check valves (565, 570). The flow into the accumulator (490) allows for excess flow from the motor or motors (210) which is not being utilized by the hydraulic actuator (balanced (280) or unbalanced (380), and not shown) which flows through detented shuttle valve (150) through port A (154) exiting port C (152) and is stored in the accumulator (490). Alternatively available stored energy in accumulator (490) is available to actuate the hydraulic actuator (balanced (280) or unbalanced (380), not shown) as needed by flow through the detented shuttle valve (150) through port C (152) exiting port A (154). Excess energy available from the hydraulic actuator (balanced (280) or unbalanced (380), not shown) can be stored in the accumulator (490) by flowing through the detented shuttle valve (150) going into port A (154) and exiting port C (152). Stored energy in the accumulator (490) can be utilized to generate energy as required by the motor (210) by flowing through the detented shuttle valve (150) with the flow flowing into port C (152) and exiting port A (154) to the motor (210) and in this case the CW outlet port (114). This forward and reverse flow path system is operational with or without an accumulator (490).

[0108] In addition, flow is blocked by a shuttle (157) and port B sealing O rings (159) from exiting port B (156). In this case there is also an upper pilot operated check valve (570) which is in the blocked condition.

[0109] For FIG. 5C the system now operates in the CCW direction with the same condition existing regarding the second return flow path in that it is enabled by the high pressure flow line connected to the upper pilot operated check valve (570) specifically to upper pilot operated check valve port J, herein port J (573) which opens the upper pilot operated check valve (570), shown in further detail in FIG. 5D, allowing bi-directional flow between the upper pilot operated check valve port K, herein port K (571) and upper pilot operated check valve port L, herein port L (572). This allows returning flow from the upper bi-directional port (140) through second optional fluid flow filter (135) to the upper pilot operated check valve (570) but specifically to and through port K (571) thereby exiting port L (572). Completing the flow path the flow continues to motor (210) which is a requirement for the proper operation of the motor(s) (210) as described. In contrast to FIG. 5A, the lower pilot operated check valve (565) is in the blocked condition.

[0110] Further for FIG. 5C, there are two distinct return flow paths. The first return fluid flow path returns from the actuator (not shown) to the lower bi-directional port (160) through the third optional fluid flow filter (165) to the motor (210) and specifically CCW outlet port (116) through the first optional fluid flow filter (122). It is critical here that the flow through the motor (210) must have an exactly equal flow entering CW outlet port (114) as is exiting CCW outlet port (116). Without this condition, the motor (210) will begin to cavitate and operate improperly or abnormally (as opposed to operating properly or normally).

[0111] For FIG. 6A, HPU system VI (600) is provided, referring back to FIG. 5A with the addition of a single pair of second upper and lower pilot operated check valves (shown as (680) and (675) respectively) with the purpose of blocking and isolating the actuator or user device (not shown) which would reside between the upper and lower bi-directional ports (140 and 160). The flow path differs from FIG. 5A (CW flow direction) as follows; in this case, flow from the motor (210) and out of the CW outlet port (114) is directed through the second upper pilot operated check valve (680), as provided in expanded detail in FIG. 6B, to upper bi-directional port (140). Specifically entering second upper pilot operated check valve port M, herein port M (681) and exiting second upper pilot operated check valve port N, herein port N (682) in the forward flow direction of the second upper pilot operated check valve (680). The pressure on the second upper pilot operated check valve port O, herein port O (683) is inconsequential in this specific mode (static low pressure).

[0112] Regarding the first returning flow path from the lower bi-directional port (160), fluid flows through lower pilot operated check valve (565) specifically entering port H (566) exiting port I (567) and proceeding to the motor (210) and to the outlet CCW port (116). This flow path is enabled by the high pressure flow line connected to the lower pilot operated check valve (565) specifically to pilot port (678) which opens check valve (675) allowing bi-directional flow between ports (677) and (676). The second returning flow path is unchanged from that described above in FIG. 5A.

[0113] For FIG. 6C flow is in the opposite direction from that shown in FIG. 6A. Referring back to FIG. 5C, FIG. 6C provides the addition of a single pair of second upper and lower pilot operated check valves shown as (680 and 675) with the purpose of blocking and isolating the actuator or user device (not shown) which would reside between the upper and lower bi-directional ports (140 and 160). The flow path differs from FIG. 5C (CCW flow direction) as follows; in this case, flow from the motor (210) and out of the CCW outlet port (116) is directed through the second lower pilot operated check valve (675) to the lower bi-directional port (160). Specifically entering, as provided in detail in FIG. 6B, the second lower pilot operated check valve port P, herein port P (676) and exiting the second lower pilot operated check valve port Q, herein port Q (677) in the forward flow direction of the second lower pilot operated check valve (675). The pressure on the second lower pilot operated check valve port R, herein port R (678) is inconsequential in this specific mode.

[0114] Regarding the first returning flow path from the upper bi-directional port (140), fluid flows through second upper pilot operated check valve (680) specifically entering port N (682) exiting port M (681) and proceeding into the motor (210) and CW outlet port (114). This flow path is enabled by the high pressure static line connected to the second upper pilot operated check valve (680) specifically to pilot port O (683) which opens the second upper pilot operated check valve (680) allowing bi-directional flow between ports M and N (681) and (682) respectively. The second returning flow path is unchanged from that described above in FIG. 5C.

[0115] FIG. 6D illustrates the same schema as FIGS. 6A and 5C, however in a completely static flow situation which provides for blocking of flows and pressures to and from the upper and lower bi-directional ports (140) and (160). In this instance, leakage through the motor seal inlet port (112) occurs and drains the high pressure from the CW outlet and CCW outlet ports (114 and 116). This relieves pressure from all pilot operated check valve (570, 565, 675, 680) ports (668,673,678,683). Control of the speed and time for which pressure drainage occurs is also part of the present disclosure.

[0116] FIGS. 7A and 7B, HPU system VII (700) generating a CW and CCW fluid flow, are identical to schemas as presented in FIGS. 6A and 6C with the exception that the lower bi-directional port (160) is blocked and unused or may be connected to a small single ended piston to unlock one or more mechanical features of the packer (not shown). This is a particular system that is useful for some hydraulic devices such as packer devices (710) which may exist with only singular hydraulic ports. FIG. 7A is for flow in the CW direction and FIG. 7B is for flow in the CCW direction. In the CW direction, there is fluid supplied from the reservoir (191) to the hydraulic device, shown as packer device (710). Alternatively in the CCW direction, fluids are removed from the hydraulic device, shown as packer device (710) and sent back to the reservoir (191) without going through the motor (210).

[0117] FIG. 7C illustrates the same schema as FIGS. 7A and 7B with the condition that the pilot operated check valves (570, 575, 675, 680) are blocking to ensure no movement (i.e. stationary condition) of the packer device (710) without any energy requirement from the motor (210).

[0118] In some embodiments, the devices and systems described herein can be configured for use only as a compressor. For example, in some embodiments, a compressor device described herein can be used as a compressor in a natural gas or oil pipeline, a natural gas or oil storage compressor, or any other industrial application that requires compression of a fluid. In another example, a compressor device described herein can be used for compressing gases such as carbon dioxide. For example, carbon dioxide can be compressed in a process for use in enhanced oil recovery or for use in carbon sequestration. In another example, a compressor device described herein can be used for compressing air. For example, compressed air can be used in numerous applications which may include cleaning applications, motive applications, ventilation applications, air separation applications, cooling applications, amongst others.

[0119] In some embodiments, the devices and systems described herein can be configured for use only as an expansion device. For example, an expansion device as described herein can be used to generate electricity or to modify the pressure of a fluid, also referred to as pressure regulation. In some embodiments, an expansion device as described herein can be used in a natural gas transmission and distribution system or an oil recovery system or both. For example, at the intersection of a high pressure (e.g., 500 psi) transmission system and a low pressure (e.g., 50 psi) distribution system, energy can be released where the pressure is stepped down from the high pressure to a low pressure. An expansion device as described herein can use the pressure differential to generate electricity. In other embodiments, an expansion device as described herein can be used in other gas systems to harness the energy from high to low pressure regulation. By use of the bi-directional capabilities of the system(s) described herein, it is possible to provide compression and/or expansion devices (also referred to herein as compression/expansion devices) according to an embodiment. A compression/expansion device can include one or more pneumatic cylinders, one or more pistons, at least one actuator, a controller and, optionally, a liquid management system such as a reservoir. The compression/expansion devices can be used, for example, in a compressed air energy storage (CAES) system.

[0120] A system for compression and/or expansion of fluids can include any suitable combination of systems or portions thereof, described in FIGS. 1-7 above. For example, in some embodiments, such a system can include any combination of system elements. For example, a system can include two or more valves or valve combinations in an in-line configuration and/or two or more valves in a stacked configuration. Additionally, a system can include one, two, three, four, or more valves per stage of compression/expansion required to achieve the necessary movement of the mechanical (user) devices as determined by the user.

[0121] The devices and systems described herein can be implemented in a wide range of sizes and operating configurations. In other words, the physics and fluid mechanics of the system do not depend on a particular system size. This estimated power range results from a system design constrained to use current commercially available components, manufacturing processes, and transportation processes. Larger and/or smaller system power may be preferred if the design uses a greater fraction of custom, purpose-designed components. Moreover, system power also depends on the end-use of the system. In other words, the size of the system may be affected by whether the system is implemented in the compressor/expander mode or whether the system is being used to deliver only compression or only expansion.

[0122] Additionally, the HPU devices according to one or more of the embodiments can be configured to compress a high volume of gas into a lower volume. Devices and systems used to compress and/or expand a gas can be configured to operate in a compression mode to compress fluids up to at least 10,000 psi.

[0123] Devices and systems used to compress and/or expand a gas can be configured to operate in an expansion mode to expand a gas such that the compressed gas from the compressed gas storage chamber has a pressure ratio to that of the expanded gas of 250:1. In some embodiments, a compression/expansion device is configured to expand a gas through two or three stages of expansion.

[0124] Devices and systems used to compress and/or expand a fluid including air, and gas, and/or to pressurize and/or pump a fluid, such as water, can release and/or absorb heat during, for example, a compression or expansion cycle. In some embodiments, one or more pneumatically or electrically actuated valves can include a heat capacitor for transferring heat to and/or from the gas as it is being compressed/expanded. In some embodiments, the heat transfer element can be a thermal capacitor that absorbs and holds heat released from a gas that is being compressed, and then releases the heat to a gas or other fluid at a later time. In some embodiments, the heat transfer element can be a heat transferring device that absorbs heat from a liquid that is being compressed, and then facilitates the transfer of the heat outside of the device.

[0125] In another example, heat can be transferred from and/or to gas that is compressed and/or expanded by adding and/or removing liquid (e.g., water) to/from within a pneumatic cylinder. A gas/liquid or gas/heat element interface may move and/or change shape during a compression and/or expansion process in a pneumatic cylinder. This movement and/or shape change may provide a compressor/expander device with a heat transfer surface that can accommodate the changing shape of the internal areas of a pneumatic cylinder in which compression and/or expansion occurs. This movement and/or shape change may provide a compressor/expander device with a heat transfer surface that optimizes its heat transfer performance with respect to the current conditions within the pneumatic cylinder, for example, with respect to gas density, gas temperature, and/or relative temperature of gas and liquid, among others. In some embodiments, the liquid may allow the volume of gas remaining in a pneumatic cylinder after compression to be nearly eliminated or completely eliminated (i.e., zero clearance volume).

[0126] A liquid (such as water or oil or other hydraulic fluids) can have a relatively high thermal capacity as compared to a gas (such as air) such that a transfer of an amount of heat energy from the gas to the liquid avoids a significant increase in the temperature of the gas, but only incurs a modest increase in the temperature of the liquid. This allows buffering of the system from substantial temperature changes. In other words, this relationship creates a system that is resistant to substantial temperature changes. Heat that is transferred between the gas and liquid, or components of the vessel itself, may be moved from or to (for example) a pneumatic cylinder through one or more processes. In some embodiments, heat can be moved in or out of the cylinder using mass transfer of the compression liquid itself. In other embodiments, heat can be moved in or out of the cylinder using heat exchange methods that transfer heat in or out of the compression liquid without removing the compression liquid from the cylinder. Such heat exchangers can be in thermal contact with the compression liquid, components of the cylinder, a heat transfer element, or any combination thereof. Furthermore, heat exchangers may also use mass transfer to move heat in or out of the cylinder. Thus, the liquid within a cylinder can be used to transfer heat from gas that is compressed or compressing (or to gas that is expanded or expanding) and can also act in combination with a heat exchanger to transfer heat to an external environment (or from an external environment). Any suitable mechanism for transferring heat out of the device during compression and/or into the device during expansion may be incorporated into the system.

[0127] In some embodiments, a hydraulic actuator includes a hydraulic ram (a component familiar to those skilled in the art of hydraulic actuation) that connects to a pneumatic piston using a piston rod. Piston motion results when a hydraulic pump urges hydraulic fluid into and/or out of a chamber or chambers of the hydraulic ram. Component sizes depend on the power desired for the complete system, on fluid pressures, and on the hydraulic fluid pressures. The fluid pressures in the pneumatic portion of the system, and hydraulic fluid pressure in the hydraulic pump/motor are considered simultaneously in order to configure the relative sizes of hydraulic ram pistons and the pneumatic cylinder pistons. In general, the ratio of the cross sectional area of the hydraulic ram piston, to the cross sectional area of the pneumatic cylinder piston must be in proportion to the ratio of the hydraulic pump/motor operating pressure, to the pneumatic cylinder operating pressure. For example, a hydraulic pump/motor may have a maximum operating pressure of 10,000 psi, if the maximum desired fluid pressure is 2500 psi, then the ratio between hydraulic ram piston cross sectional area to the pneumatic cylinder piston may be no less than 100 divided by 400, and in fact should be greater than this ratio figure in order to overcome machine aspects such as component friction and the like. In addition, the ratio of hydraulic ram piston cross section area to pneumatic piston cross section area can be modified during system operation configuring a hydraulic actuation system with more than one hydraulic ram, a concept which is described in more detail below.

[0128] In the present disclosure, the system operation may be controlled by a hydraulic controller and/or electric controller. The controller coordinates: valve actuation, pump/motor operation, fluid direction, and compression/expansion operation. During expansion operation, the controller determines the volume of fluid to admit from a reservoir into the system. By way of example, the controller may collect and evaluate system status information such as the temperatures and pressures of: the fluid storage chambers, cylinders, the fluid source and determine a preferred volume of fluid to admit from the reservoir into or out of the system. The controller may admit a fluid volume calculated to expand such that the fluid achieves a pressure roughly equivalent to the pressure of the fluid source. It is understood that it may be desirable to expand the fluid to pressures that may be greater than, or less than the pressure of the fluid source. The controllers may be used with any of many control paradigms to define overall machine operation such as: a time-based schedule for fluid volume, a time-based schedule for fluid pressure, a time-based schedule for fluid temperature, a parametrically described and controlled position evolution, pressure evolution, temperature evolution, or power consumption/generation. Those skilled in the art of controller design will understand that the possible control algorithms are virtually unlimited.

[0129] In some embodiments, one or more hydraulic actuators of a compression/expansion device may incorporate gear change or gear shift features within a single stage of compression or expansion, or during a cycle or stroke of the actuator, to optimize the energy efficiency of the hydraulic actuation. As used herein, the terms gear change or gear shift are used to described a change in the ratio of the pressure of the hydraulic fluid in the active hydraulic actuator chambers to the pressure of the fluid in the working chamber actuated by (or actuating) the hydraulic actuator, which is essentially the ratio of the pressurized surface area of the working piston(s) to the net area of the pressurized surface area(s) of the hydraulic piston(s) actuating the working piston(s). The term gear can refer to a state in which a hydraulic actuator has a particular piston area ratio (e.g., the ratio of the net working surface area of the hydraulic actuator to the working surface area of the working piston acting on, or being acted on by, the gas in a working chamber) at a given time period. Examples of suitable hydraulic actuators including gear changes or gear shifts are described in the '724 application earlier incorporated by reference. The compressor/expander system can also be used with other types of storage, including, but not limited to, tanks, underwater storage vessels, and the like.

[0130] While various embodiments of the invention have been described above, it should be understood that they have been presented by way of example only, and not limitation. Where methods and steps described above indicate certain events occurring in certain order, those of ordinary skill in the art having the benefit of this disclosure would recognize that the ordering of certain steps may be modified and that such modifications are in accordance with the variations of the invention. Additionally, certain of the steps may be performed concurrently in a parallel process when possible, as well as performed sequentially as described above. Additionally, certain steps may be partially completed before proceeding to subsequent steps. The embodiments have been particularly shown and described, but it will be understood that various changes in form and details may be made.

[0131] Although various embodiments have been described as having particular features and/or combinations of components, other embodiments are possible having any combination or sub-combination of any features and/or components from any of the embodiments described herein.