Patent Publication Number: US-10774822-B2

Title: Multiphase production boost method and system

Description:
CROSS REFERENCE TO RELATED APPLICATIONS 
     This application is a divisional of, and claims priority to and the benefit of co-pending U.S. application Ser. No. 14/956,643, filed Dec. 2, 2015, titled “Multiphase Production Boost Method and System,” which claims priority to and the benefit of U.S. Provisional Application No. 62/088,749, titled “Multiphase Production Boost Method and System,” filed Dec. 8, 2014, the full disclosure of each which is hereby incorporated by reference herein in its entirety for all purposes. 
    
    
     BACKGROUND OF THE DISCLOSURE 
     1. Field of the Disclosure 
     The field of disclosure relates to the production of a multiphase hydrocarbon-bearing fluid. More specifically, the field relates to boosting the pressure of the hydrocarbon-bearing fluid with pumps and compressors. 
     2. Description of the Related Art 
     Oil and gas production often starts with high reservoir pressure that allows a well to produce oil, gas or a combination of both, naturally. The production fluids are typically mixtures of gas, oil and water. The fraction of gas can increase as the pressure decreases, especially at or near the surface or at other locations where the pressure may drop below bubble point pressure. As the reservoir is produced and the pressure declines, the water cut increases with naturally-driven production, and the production rate drops. This problem of pressure reduction and increase in gas phase can be aggravated if the well is far from a central gathering station and the multiphase fluid is transported over long distances or hilly terrain. 
     To regain production and increase field recovery, external energy will need to be added to the production systems via either downhole artificial lift or surface pressure boosting. Artificial lift devices need to be able to operate under multiphase flow conditions. Electrical submersible pumps (ESP) are very efficient at handling liquids; however, their performance decreases in the presence of gas. 
     Multi-phase pumps (MPP) are operable to pump multiphase fluids having a combination of crude oil, water and natural gas without the need for prior separation. With MPP technology, remote separation infrastructure may be eliminated. This leads to lower infrastructure costs associated with the development of hydrocarbon reserves. As well, marginal fields located in hostile environments may also be developed more economically. 
     Existing MPP technologies include helicon-axial dynamic and twin screw positive displacement types. The helicon-axial multiphase pump includes multiple stages, where each consists of a rotating helico-shaped impeller and a stationary diffuser. This configuration is a hybrid between a dynamic pump and an axial compressor that allows a wide range of liquid flow rates and inlet gas concentration. In theory, a dynamic pump creates pressure dynamically, where shaft torque is converted into angular momentum. The differential pressure depends on motor speed and inlet fluid density. This makes dynamic pumps extremely sensitive to small changes in inlet conditions. Large changes in shaft torque under intermittent flow are common with dynamic pumps. Designs often incorporate flow homogenizers (for example, buffer tanks) to absorb liquid “slugs” and to even out fluctuations in gas density and pressure. This minimizes repetitive torque changes within the pump. In addition, variable speed drive (VFD) is used to adjust the motor speed to maintain a constant inlet pressure. 
     A twin screw MPP is a rotary positive displacement pump that includes a power shaft and an idle shaft with two screw-shell rotors per shaft. The power shaft is coupled to the motor while the idle shaft is driven by the power shaft through a timing gear on the outboard side of the pump. There are gaps between screw pairs and between the screw and the pump housing to allow abrasive handling. Production fluids enter the pump from both ends. As the screws rotate, fluid fills the volumetric chambers between the individual screw flanks. The thread profile axially transports fluids from both ends of the pump to the center, where the fluids rejoin and exit the pump through the outlet. 
     SUMMARY OF THE DISCLOSURE 
     There are issues with using MPP technology. Common issues with the technologies mainly break down along cost, complexity and reliability. Operators typically experience poor uptime and frequent maintenance during initial installation and break-in. The software and control systems for dynamic operations may be inadequate to handle the unstable dynamic behavior of the well, leading to frequent “tripping” and shutdown. The dynamic pumps have a higher-than-average trip frequency compared to all pumps. When restarting after a long shutdown, some installations experienced prolong low speed (500 rpm) operations to handle gas buildup and production fluid having a high gas oil ratio (GOR). This low efficiency production avoids over-heating due to prolong gas flow, which has poor heat transfer and lubrication compared to crude oil. System power efficiency using MPP technology is reportedly low with the highest efficiency currently at about 50-60%. 
     It is desirable to have a system and a method for handling low-pressure multiphase production fluid to produce a high-pressure multiphase fluid where reliability and efficiency are improved over the use of a multi-phase pump system. A reduction in overall operating costs not only in more consistent production but also by using technology that is more reliable and well-known is also viewed as an improvement. 
     In embodiments of this disclosure, a system for boosting the pressure of a low-pressure multiphase mixture into a high-pressure multiphase mixture is disclosed. A gas-liquid separator of the system has a gas portion and a liquid portion. The gas-liquid separator is operable to separate the low-pressure multiphase mixture into a low-pressure gas and a low-pressure liquid. The system also includes a liquids pump. The liquids pump couples to the liquid portion of the gas-liquid separator. The liquids pump is operable to convert the low-pressure liquid into a high-pressure liquid. The system includes a liquid piston compressor. The liquid piston compressor has a gas portion and a liquid portion. The liquid piston compressor is operable to compress the low-pressure gas into a high-pressure gas using the high-pressure liquid. The gas portion of the liquid piston compressor couples to the gas portion of the gas-liquid separator such that there is one-way fluid communication of the low-pressure gas from the gas-liquid separator to the liquid piston compressor. The liquid portion of the liquid piston compressor couples to the liquids pump such that there is one-way fluid communication of the high-pressure liquid from the liquids pump to the liquid piston compressor. 
     In alternate embodiments, the liquid portion of the liquid piston compressor can also couple to the liquids pump such that there is one-way fluid communication of a reduced pressure liquid from the liquid piston compressor to the liquids pump. The liquid portion of the liquid piston compressor can alternately couple to the gas-liquid separator such that there is one-way fluid communication of a reduced pressure liquid from the liquid piston compressor to the gas-liquid separator. The system can be operable to maintain the liquid piston compressor in a substantially isothermal condition. The substantially isothermal condition can be maintained using the low-pressure liquid from the gas-liquid separator. 
     In other alternate embodiments, a liquid level controller can be included that is operable to detect a liquid level within the liquid piston compressor. The liquid level controller can also operable to selectively permit the introduction of the high-pressure liquid into and to selectively permit the passing of a reduced pressure liquid from the liquid piston compressor. The liquid level controller can also be operable to selectively permit the introduction of the low-pressure gas into and to selectively permit the passing of the high-pressure gas from the liquid piston compressor. A temperature controller can alternately be included that is operable to detect a temperature within the liquid piston compressor. The temperature controller can also be operable to selectively permit the introduction of a cooling liquid to the liquid piston compressor. 
     A method for boosting the pressure of the low-pressure multiphase mixture to the high-pressure multiphase mixture includes introducing the low-pressure multiphase mixture into a pressure boost system. The low-pressure multiphase mixture comprises the low-pressure liquid and the low-pressure gas. The method includes operating the pressure boost system such that the low-pressure liquid and the low-pressure gas form from the low-pressure multiphase mixture, and a high-pressure liquid forms from the low-pressure liquid. During a charging period the low-pressure gas is introduced into, and the low-pressure liquid passes from, a liquid piston compressor. During a compression period the high-pressure liquid is introduced into the liquid piston compressor such that the low-pressure gas converts into a high-pressure gas. During a discharging period the high-pressure liquid is introduced into, and the high-pressure gas passes from, the liquid piston compressor. The high-pressure liquid and the high-pressure gas are mixed such that the high-pressure multiphase mixture forms. The method includes passing the high-pressure multiphase mixture from the pressure boost system. 
     In alternate embodiments, a pressure difference between the high-pressure liquid and the high-pressure gas is not substantial. The pressure boost system can be operated such that the liquid piston compressor during the compression period is maintained at a substantially isothermal condition. The compression period can start at the detection of a low liquid level and end at the detection of a high level liquid level within the liquid piston compressor. The charging period can start at the detection of a high liquid level and end at the detection of a low level liquid level within the liquid piston compressor. During the compression period, a cooling liquid can be introduced to the liquid piston compressor. During both the compression and discharge periods a cooling liquid can be introduced to the liquid piston compressor such that the liquid piston compressor is maintained at a substantially isothermal condition. The pressure boost system can comprise more than one liquid piston compressor and when a first liquid piston compressor is operating in a charging period, a second liquid piston compressor can be operating in a discharging period. 
     The methods and the systems disclosed herein are for boosting production of a multi-phase fluid comprising crude oil, natural gas and formation water. The systems separate the gas-liquid mixture into a low-pressure gas and a low-pressure liquid. A conventional-type liquid pump is used to increase the pressure of the liquid, which is a combination of crude oil and formation water, to a high-pressure liquid. The gas pressure is boosted using a liquid piston compressor, where the liquid driving the liquid piston compressor is the high-pressure liquid. The high-pressure gas and the high-pressure liquid are recombined into a multi-phase product and passed from the system. Optionally, the liquid piston compressor is operable to cool such that isothermal or near-isothermal compression occurs. The systems offer compactness, higher reliability and higher energy efficiency with well-understood and reliable components. 
     The systems offer a solution by permitting the use of known separators and standard liquid pumps to handle a multiphase production. The low-pressure gas is separated before the intake of the liquids pump and it is reintroduced after the high-pressure liquid discharges. The low-pressure gas is compressed using the liquid piston compressor that optionally may operate under near-isothermal to isothermal gas conditions to achieve a high power efficiency. Liquid piston compression overcomes the poor heat transfer issue associated with typical mechanical compressions such as reciprocating piston compressors, and the lack of moving mechanical parts adds reliability to the operating system. 
     The disclosed methods and systems are useful for wet gas compression, and for off-shore and subsea and downhole applications. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       These and other features, aspects, and advantages of the present disclosure are better understood with regard to the following Detailed Description of the Preferred Embodiments, appended Claims, and accompanying Figures, where: 
         FIG. 1  shows a schematic diagram of an embodiment of the production boost system for performing the production boost method; 
         FIGS. 2A-C  show a schematic diagram of an embodiment of the production boost system performing an embodiment of the production boost method; and 
         FIG. 3  shows a schematic diagram of another embodiment of the production boost system for performing the production boost method. 
         FIG. 1-3  shows an embodiment of the method of use and a system for boosting pressure of a multiphase fluid.  FIG. 1-3  and its description facilitate a better understanding of the boosting pressure system and its method of use. In no way should  FIGS. 1-3  limit or define the scope of the embodiments of this disclosure.  FIG. 1-3  are a simple diagram for ease of description. 
     
    
    
     In the accompanying Figures, similar components or features, or both, may have a similar reference label. Further, various components of the same type may be distinguished by following the reference label with a secondary label or mark of distinction, including a “‘” or an alphanumeric character. 
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 
     The Specification, which includes the Summary of Disclosure, Brief Description of the Drawings and the Detailed Description of the Preferred Embodiments, and the appended Claims refer to particular features (including process or method steps) of the embodiments of this disclosure. Those of skill in the art understand that the embodiments of this disclosure include all possible combinations and uses of particular features described in the Specification. Those of skill in the art understand that the disclosure is not limited to or by the description of embodiments given in the Specification. The inventive subject matter is not restricted except only in the spirit of the Specification and appended Claims. 
     Those of skill in the art also understand that the terminology used for describing particular embodiments does not limit the scope or breadth of the disclosure. In interpreting the Specification and appended Claims, all terms should be interpreted in the broadest possible manner consistent with the context of each term. All technical and scientific terms used in the Specification and appended Claims have the same meaning as commonly understood by one of ordinary skill in the art to which this disclosure belongs unless defined otherwise. 
     As used in the Specification and appended Claims, the singular forms “a”, “an” and “the” include plural references unless the context clearly indicates otherwise. The verb “comprises” and its conjugated forms should be interpreted as referring to elements, components or steps in a non-exclusive manner, and the illustrative embodiments disclosed suitably may be practiced in the absence of any element which is not specifically disclosed, including as “consisting essentially of” and “consisting of”. The referenced elements, components or steps may be present, utilized or combined with other elements, components or steps not expressly referenced. The verb “couple” and its conjugated forms means to complete any type of required junction, including electrical, mechanical or fluid, to form a singular object from two or more previously non-joined objects. If a first device couples to a second device, the connection can occur either directly or through a common connector. “Optionally” and its various forms means that the subsequently described event or circumstance may or may not occur. The description includes instances where the event or circumstance occurs and instances where it does not occur. “Operable” and its various forms means fit for its proper functioning and able to be used for its intended use. “Associated” and its various forms means something connected with something else because they occur together or that one produces the other. “Detect” and its conjugated forms should be interpreted to mean the identification of the presence or existence of a characteristic or property. “Determine” and its conjugated forms should be interpreted to mean the ascertainment or establishment through analysis or calculation of a characteristic or property 
     Spatial terms describe the relative position of an object or a group of objects relative to another object or group of objects. The spatial relationships apply along vertical and horizontal axes. Orientation and relational words, including “uphole” and “downhole”, are for descriptive convenience and are not limiting unless otherwise indicated. “Substantial” means equal to or greater than 10% by the indicated unit of measure. “Significant” means equal to or greater than 1% by the indicated unit of measure. 
     Where the Specification or the appended Claims provide a range of values, it is understood that the interval encompasses each intervening value between the upper limit and the lower limit as well as the upper limit and the lower limit. The disclosure encompasses and bounds smaller ranges of the interval subject to any specific exclusion provided. 
     Where the Specification and appended Claims reference a method comprising two or more defined steps, the defined steps can be carried out in any order or simultaneously except where the context excludes that possibility. 
     
       FIG. 1 
     
       FIG. 1  shows a schematic diagram of an embodiment of the production boost system for performing the production boost method. Production boost system  100  includes gas-liquid separator  10 , liquids pump  12 , liquid piston compressor  14 , low-pressure gas inlet valve  16 , high-pressure gas outlet valve  18 , high-pressure liquid supply valve  20 , liquid recycle valve  22 , liquid level controller  24  and liquid orifice plate  26  are coupled together such that low-pressure gases and low-pressure liquids are pressurized into high-pressure liquids and gases. Production boost system  100  is operable to receive a low-pressure gas, oil, and water multiphase mixture that is introduced through introduction line  30  and to pass as a product that is a high-pressure gas, oil, and water mixture through production line  32 . 
     As an example, when the low-pressure multiphase mixture is introduced into the production boost system, the low-pressure multiphase mixture can have a pressure in a range from atmospheric pressure to up to 1000 psig, and can have a temperature in a range from 40-200 degrees Fahrenheit. If the low-pressure multiphase mixture is from an oil production system, the gas-liquid ratio can be, as an example, 50-900 SCF/STB. If the low-pressure multiphase mixture is from a gas condensate system, the condensate gas ratio can be, for example, 50-350 BBL/MMSCF and the water gas ratio can be, for example, 2-10 BBL/MMSCF. The low-pressure multiphase mixture can have, as an example, a water cut of 0-80%. 
     Low-pressure gas G is located in gas portion  9  and lower pressure liquid L is located in liquid portion  11  of gas-liquid separator  10 . The multiphase mixture introduced through introduction line  30  separates into low-pressure gas G and low-pressure liquid L, where the low-pressure liquid L includes both crude oil or condensates as well as water or brine. Gas-liquid separator  10  may be any type of separator mechanism that is operable to separate vapors and gases from liquids, including horizontal or vertical gravity separators, which include heated, cooled, atmospheric and vacuum distillation towers and packed columns; cyclone separators; and inline separators. 
     Liquids pump  12  couples with liquid portion  11  of gas-liquid separator  10  such that at least a portion of the liquid intake into liquids pump  12  is from gas-liquid separator  10 . Liquids pump  12  may be any type of conventional liquid conveying mechanism that imparts greater force or pressure into the liquid that it discharges than the liquid that it draws inward, including centrifugal pumps and displacement pumps. Liquids pump  12  is not a multiphase pump (both gas and liquid simultaneously); rather, liquids pump  12  is a standard liquid-conveying pump, which improves its reliability and reduces both its operational and replacement costs. When high-pressure liquid HL is discharged from liquids pump  12 , high-pressure liquid HL can have a pressure, as an example, in a range of 300-1200 psig. 
     Low-pressure gas inlet valve  16  is located between and is operable to permit low pressure gas G to pass in one-way communication from gas-liquid separator  10  to gas portion  13  of liquid piston compressor  14 . Low-pressure gas inlet valve  16  is also operable to deny high-pressure gas HG from passing from liquid piston compressor  14  to gas-liquid separator  10 . The check valve for low-pressure gas inlet valve  16  has a spring tension (low-pressure differential tension setting) as part of its valve flapper mechanism such that low-pressure gas from gas-liquid separator  10  is permitted to flow towards liquid piston compressor  14  when a sufficient differential pressure exists between gas-liquid separator  10  and liquid piston compressor  14 . The low pressure differential tension setting is such that gas communication from liquid piston compressor  14  to gas-liquid separator  10  does not occur: the low-pressure differential tension setting is not overcome by a switch in flow direction. High-pressure gas outlet valve  18  operates in a similar manner: it has a high-pressure differential tension setting that permits high pressure gas HG to pass from gas portion  13  of liquid piston compressor  14  in one-way communication towards production line  32  when a sufficient pressure differential exists. High-pressure gas outlet valve  18  is also operable to deny gas having insufficient pressure from passing towards production line  32 . 
     In the embodiment of the system shown in  FIG. 1 , low-pressure gas inlet valve  16  and high-pressure gas outlet valve  18  are both check valves. In another embodiment of the system, either or both check valves are replaced with a control valve. In such an embodiment, the control valve is operated such that no backflow of gas to either gas-liquid separator  10  or liquid piston compressor  14 , respectively, occurs. The types of control valves for either or both low-pressure gas inlet valve  16  and high-pressure gas outlet valve  18  includes ball, plug, gate and globe valves. The valve actuators for such control valves can be electric or pneumatic. In such an embodiment, a pressure controller monitors the gas pressures associated with gas upstream of the control valve low-pressure gas inlet valve  16 , between the control valve of low-pressure gas inlet valve  16  and high-pressure gas outlet valve  18  and downstream of the control valve of high-pressure gas outlet valve  18  such that production boost system  100  is operable to open and close the control valve of low-pressure gas inlet valve  16  and high-pressure gas outlet valve  18  during the appropriate periods of performing an embodiment of the production boost method. 
     In another embodiment of the system, low-pressure gas inlet valve  16  and high-pressure gas outlet valve  18  are substituted for a 3-way valve that is operable to switch position depending on the gas operation associated with liquid piston compressor  14  (filling, letting down). 
     In an embodiment of the system, the liquid portion of the liquid piston compressor  14  also couples to the liquids pump  12  such that there is one-way fluid communication of a reduced pressure liquid from the liquid piston compressor  14  to the liquids pump  12 . The reduced pressure liquid may pass to liquids pump  12 , gas-liquid separator  10  or both depending on production boost system  100  operations. Fluids will generally travel from areas of higher pressure towards areas of lower pressure. The reduced pressure liquid can have a lower pressure than the low-pressure gas, and the movement of reduced pressure liquid out of the liquid piston compressor can cause a pressure sink within the liquid piston compressor  14 , both of which can help pull the low-pressure gas into liquid piston compressor  14 , helping with the charging period. Depending on the number and size of the liquid piston compressors  14  and the gas-liquid ratio, it can take a number of minutes to perform each of the charging periods and the compression periods. 
     Liquid recycle valve  22  is located between and is operable to selectively permit reduced pressure liquid to pass from liquid piston compressor  14  during the charging period. The reduced pressure liquid passes in one-way communication from liquid portion  15  of liquid piston compressor  14 . The reduced pressure liquid is not high-pressure liquid HL because during the charging period the gas introduced into liquid piston compressor  14  is low-pressure gas G, which helps to force reduced pressure liquid from liquid piston compressor  14 . Liquid recycle valve  22  is also operable to deny the low-pressure liquid L from bypassing liquids pump  12  and entering liquid piston compressor  14  directly from gas-liquid separator  10 . 
     In another embodiment of the system, the liquid portion of the liquid piston compressor couples to the gas-liquid separator such that there is one-way fluid communication of the reduced pressure liquid from the liquid piston compressor to the gas-liquid separator. During cycling of liquid piston compressor  14 , gas may become entrained or dissolve into the liquid within liquid piston compressor  14 . Any gases recycled to the fluid inlet line for liquids pump  12  may come out of solution and form bubbles, which causes cavitation. Cavitation over time will break down liquids pump  12  impeller and erode the pump housing. To avoid gas entrainment in the fluid inlet line for liquids pump  12 , the reduced pressure liquid passing from liquid recycle valve  22  optionally is directed back to gas-liquid separator  10  through recycle valve  28  line. Recycling reduced pressure liquid back to gas-liquid separator  10  allows the reduced pressure liquid to release any entrained gases in gas-liquid separator  10  instead of in the low pressure conditions at the inlet draw of liquids pump  12 . 
     High-pressure liquid supply valve  20  is located between and is operable to permit high-pressure liquid HL to pass in one-way communication from liquids pump  12  to liquid portion  15  of liquid piston compressor  14 . For low gas to oil ratio systems, the amount of high-pressure liquid passing from liquids pump  12  to liquid portion  15  of liquid piston compressor  14  can be as low as 10%. For higher gas to oil ratio systems, the amount of high-pressure liquid passing from liquids pump  12  to liquid portion  15  of liquid piston compressor  14  can be as high as 90%. High-pressure liquid supply valve  20  is also operable to deny low-pressure liquid L from bypassing liquids pump  12  and into production line  32 . 
     High-pressure liquid supply valve  20  and liquid recycle valve  22  may include various types of valves: ball, plug, gate and globe. The valve actuators can be electric or pneumatic. 
     In another embodiment of the system, high-pressure liquid supply valve  20  and liquid recycle valve  22  are substituted for a 3-way valve that is operable to switch position depending on the liquid operation associated with liquid piston compressor  14  (filling, letting down). 
     Gas, especially high-pressure gas HG is located in gas portion  13  and liquid, especially high-pressure liquid HL, is located in liquid portion  15  of liquid piston compressor  14 . Gas portion  13  couples with gas portion  9  through low-pressure gas inlet valve  16  and production line  32  through high-pressure gas outlet valve  18 . Liquid portion  15  couples with liquid portion  11  through liquids pump  12  and high-pressure liquid supply valve  20 , and with production line  32  through liquids pump  12  and liquid recycle valve  22 . 
     In an embodiment of the system, the production boost system includes a liquid level controller that is operable to detect a liquid level within the liquid piston compressor. Production boost system  100  includes liquid level controller  24  that is signally coupled to several portions of liquid piston compressor  14  for monitoring the liquid level conditions during cycling of liquid piston compressor  14 . 
     Liquid level set points for liquid piston compressor  14  may maximize the use of liquid piston compressor  14  volumetric capacity while also preventing liquid overflow (excessive liquid) or gas blow through (insufficient liquid). Maximizing volumetric capacity between the low set point and the high set point maximizes system efficiency for each stroke (charging, compressing, and discharging) of liquid piston compressor  14 . In an embodiment of the system, a high level set point for liquid level controller  24  is 90% of the volumetric capacity of liquid piston compressor  14  and a low level set point is 10% of the volumetric capacity of liquid piston compressor  14 . 
     Liquid level controller  24  is in signal communication with both high-pressure liquid supply valve  20  and liquid recycle valve  22 . Liquid level controller  24  is operable to modify the position of each valve. In an embodiment of the system, the liquid level controller is also operable to selectively permit the introduction of the high-pressure liquid into and to selectively permit the passing of a reduced pressure liquid from the liquid piston compressor. In an embodiment of the method, the production boost system changes from charging the liquid piston compressor with low-pressure gas during the charging period, to compressing the charged gas upon detection by the level controller of a liquid level at the low level set point during the compression period. In an embodiment of the method, the production boost system changes from discharging the high-pressure gas to charging the liquid piston compressor with low-pressure gas upon detection by the level controller of a liquid level at the high level set point. 
     In an embodiment of the system, liquid level controller  24  is also in signal communication with both low-pressure gas inlet valve  16  and high-pressure gas outlet valve  18 . In such an embodiment, the liquid level controller is also operable to selectively permit the introduction of the low-pressure gas into and to selectively permit the passing of the high-pressure gas from the liquid piston compressor. In an embodiment of the system, the compression of charged gas is an isothermal or near-isothermal process, where the temperature of the gas remains constant. Extra cooling may be required to achieve such an isothermal compression. In other alternate embodiments, the compression of charged gas is not an isothermal or near-isothermal process and no extra cooling is required during the compression period. 
     To re-comingle the higher-pressure liquid and gas, the pressures of the liquid and the gas are similar. The high-pressure liquid has a higher pressure than the high-pressure gas during mixing into the high-pressure multiphase mixture. In an embodiment of the method, the pressure difference between the high-pressure liquid and the high-pressure gas is not substantial. A pressure reduction device, including liquid orifice plate  26 , provides physical resistance to the liquid, which results in a pressure drop across the liquid orifice plate  26 . Reducing the liquid pressure allows both the high-pressure liquid and high pressure gas to be at similar values, permitting them to be comingled and recombined into the produced higher-pressure multi-phase fluid. 
     
       FIGS. 2A-C 
     
       FIGS. 2A-C  show a schematic diagram of an embodiment of the production boost system performing an embodiment of the production boost method. Production boost system  200  is similar in configuration to production boost system  100  except for the lack of recycle valve  28  line, which is omitted for the sake of clarity of discussing the steps of the production boost method. 
     The low-pressure gas, oil, and water multiphase mixture is continually introduced through introduction line  30  into production boost system  200 . Production boost system  200  operates gas-liquid separator  10  such that the low-pressure gas, oil, and water multiphase mixture separates into low-pressure liquid L and low-pressure gas G. Production boost system  200  operates liquids pump  12  such that it conveys low-pressure liquid L from gas-liquid separator  10  and converts it into high-pressure liquid HL. Production boost system  200  operates liquid piston compressor  14  using high-pressure liquid HL to compresses low-pressure gas G into high-pressure gas HG. Production boost system  200  combines high-pressure liquid HL and high-pressure gas HG and passes the product high-pressure gas, oil and water multiphase mixture through production line  32 . 
     During a charging period, production boost system  200  introduces low-pressure gas G into liquid piston compressor  14 .  FIG. 2A  shows low-pressure gas G being introduced into liquid piston compressor  14 . In an embodiment of the method, the charging period starts at the detection of a high liquid level and ends at the detection of a low level liquid level within the liquid piston compressor. During the charging period, liquid recycle valve  22  operates and transitions into open liquid recycle valve  22 ′ (black), forming a liquid fluid pathway between liquid piston compressor  14  and the suction line for liquids pump  12 . The operation of liquids pump  12  provides a pressure drive for reduced pressure liquid in liquid piston compressor  14  to move towards liquids pump  12  and vacate liquid piston compressor  14  (arrow  50 ). The one-way pressure differential between gas-liquid separator  10  and liquid piston compressor  14  is sufficient to permit low-pressure gas inlet valve  16  to operate (overcoming its low-pressure gas differential tension setting) and transition into open low-pressure gas inlet valve  16 ′ (open). Open low-pressure gas inlet valve  16 ′ permits low-pressure gas G to flow from gas-liquid separator  10  into liquid piston compressor  14 . 
     During a compression period, production boost system  200  introduces high-pressure liquid HL into liquid piston compressor  14  while maintaining the previously introduce gas in a fixed volume. In an embodiment of the method, the compression period starts at the detection of a low liquid level and ends at the detection of a high level liquid level within the liquid piston compressor. In an embodiment of the method, a cooling liquid is introduced to the liquid piston compressor during the compression period.  FIG. 2B  shows production boost system  200  operating such that high-pressure liquid HL compresses low-pressure gas G such that high-pressure gas HG forms. High-pressure liquid supply valve  20  operates and transitions into open high-pressure liquid supply valve  20 ′ (black), forming a liquid fluid pathway between liquid piston compressor  14  and the discharge line for liquids pump  12 . Also, open liquid recycle valve  22 ′ operates and transitions into liquid recycle valve  22  (white), closing the previously opened pathway between liquid piston compressor  14  and the suction line for liquids pump  12 . This combination of control valve operations provides a pressure drive for high-pressure liquid HL to move from liquids pump  12  into liquid piston compressor  14 . Open low-pressure gas inlet valve  16 ′ operates and transitions into low-pressure gas inlet valve  16  (closed), isolating the previously introduced low-pressure gas G between low-pressure gas inlet valve  16 , high-pressure gas outlet valve  18 , and high-pressure liquid HL in liquid piston compressor  14 . Low-pressure gas inlet valve  16  closes due to the one-way pressure differential between gas-liquid separator  10  and liquid piston compressor  14  not being sufficient to overcome the low-pressure gas differential tension setting of the low-pressure gas inlet valve  16 . The movement of high-pressure liquid HL against low-pressure gas G in liquid piston compressor  14  drives the fluid level in liquid piston compressor  14  upwards (arrow  52 ). 
     Upon liquid level controller  24  detecting a low liquid level condition within liquid piston compressor  14 , production boost system  200  operates high-pressure liquid supply valve  20  such that high-pressure liquid HL is introduced into liquid piston compressor  14 . In addition, production boost system  200  optionally operates low-pressure gas inlet valve  16  such that low-pressure gas G is no longer introduced into liquid piston compressor  14 . Low-pressure gas G is compressed into high-pressure gas HG as previously provided for in the description of  FIG. 2B . 
     During a discharge period, production boost system  200  passes high-pressure gas HG from liquid piston compressor  14 .  FIG. 2C  shows high-pressure gas HG formed in liquid piston compressor  14  and production boost system  200  operating such that high-pressure gas HG discharges towards production line  32 . The pressure of high-pressure gas HG in liquid piston compressor  14  is sufficient to overcome the high-pressure gas differential tension setting of high-pressure gas outlet valve  18 . High-pressure gas outlet valve  18  operates and transitions into open high-pressure gas outlet valve  18 ′ (open), permitting high-pressure gas HG to flow from liquid piston compressor  14  as the high-pressure liquid HL level continues to elevate (arrow  54 ). Open high-pressure liquid supply valve  20 ′ remains open to provide drive against high-pressure gas HG during discharge. 
     In an embodiment of the method, during both the compression and discharge periods a cooling liquid is introduced to the liquid piston compressor such that the liquid piston compressor is maintained at a substantially isothermal condition. 
     Upon liquid level controller  24  detecting a high liquid level condition within liquid piston compressor  14 , production boost system  200  operates open high-pressure liquid supply valve  20 ′ such that high-pressure liquid HL is no longer introduced into liquid piston compressor  14  by closing the valve. In addition, production boost system  200  optionally operates liquid recycle valve  22  such that a reduced pressure liquid passes from liquid piston compressor  14 . The production boost system  200  operates open high-pressure gas outlet valve  18 ′ such that it closes into high-pressure gas outlet valve  18 . High-pressure gas outlet valve  18  prevents the passing of high-pressure gas HG towards production line  32 . In a further embodiment of the method, production boost system  200  operates such that low-pressure gas G charges liquid piston compressor  14  as previously provided in the description of  FIG. 2A . 
     In operation, the gas charging, compression, and discharging steps outline a cyclical, repeating process for operating production boost system. An embodiment of the production boost system includes more than one liquid piston compressor. In an embodiment of the method, the pressure boost system comprises more than one liquid piston compressor and while a first liquid piston compressor operates in a charging period a second liquid piston compressor operates in a discharging period. Operating such a system having several liquid piston compressors in parallel and in staggered operation (one charging, one compressing, one discharging simultaneously) may reduce disruption of the operation from a centralized liquid-gas separator, liquids pump and product discharge line. Several liquid piston compressors acting in parallel may also prevent downstream slugging from cyclical discharging operations. Such a system maintains a uniform flow of high-pressure gas for forming the production multiphase mixture. 
     
       FIG. 3 
     
       FIG. 3  shows a schematic diagram of another embodiment of the production boost system for performing the production boost method. Production boost system  300  is of a similar configuration as production boost system  100  shown in  FIG. 1  and production boost system  200  shown in  FIGS. 2A-C ; however, liquid piston compressor  14  is replaced with isothermal liquid piston compressor  314 . Production boost system  300  also includes cooling liquid feed line  370 , liquid return line  372 , flow control valve  374  and temperature controller  380 . In an embodiment of the system, the production boost system is operable to maintain the liquid piston compressor in a substantially isothermal condition. In an embodiment of the system, the production boost system is operable to maintain the liquid piston compressor in a significantly isothermal condition. In an embodiment of the system, the production boost system is operable to maintain the liquid piston compressor in an isothermal condition. 
     Production boost system  300  includes isothermal liquid piston compressor  314 . As low-pressure gas G is compressed during the compression period within the volume bound by low-pressure gas inlet valve  16 , high-pressure gas outlet valve  18  and isothermal liquid piston compressor  314 , without some sort of cooling the temperature of the compressing gas will increase. A temperature increase in the gas represents a loss of energy—energy that could have been transformed into higher pressure. To improve system efficiency in compressing the low-pressure gas to the high-pressure gas, production boost system  300  is operable to use low-pressure liquid L to make the conditions for the compressing gas within isothermal liquid piston compressor  314  as isothermal or as close to isothermal as feasible. In an embodiment of the system, the substantially isothermal condition is maintained using the low-pressure liquid from the gas-liquid separator. 
     For production boost system  300 , isothermal liquid piston compressor  314  is akin to a single pass “tube and shell” heat exchanger. The “tube” portion of liquid piston compressor  314  acts as several liquid piston compressors  360  operating in parallel similar to liquid piston compressor  14  of  FIGS. 1-2C . In an embodiment of the system, the exterior surface of several liquid piston compressors  360  includes radiative fins that are operable to distribute heat into a liquid within shell fluid void  366 . 
     The “shell” side includes inlet head  362 , outlet head  364  and shell fluid void  366 . Inlet head  362 , outlet head  364  and shell fluid void  366  are coupled such that liquid fluid flows through each without restriction. Shell fluid void  366  is defined as the void volume inside the exterior shell of isothermal liquid piston compressor  314  and is bound by the exteriors of several liquid piston compressors  360 , inlet head  362  and outlet head  364 . In an embodiment of the system, shell fluid void  366  may be further divided by internal baffles to enhance the liquid fluid contact with the exterior surface of several liquid piston compressors  360 . Inlet head  362 , outlet head  364  and shell fluid void  366  are operable to receive low-pressure liquid L upstream of liquids pump  12 , high-pressure liquid HL downstream from liquids pump  12  or a combination of both. Shell fluid void  366  is operable to permit concurrent or counter-current liquid flow. 
       FIG. 3  shows isothermal liquid piston compressor  314  coupled to gas-liquid separator  10  through the shell side by cooling liquid feed line  370  and liquid return line  372 . Cooling liquid feed line  370  permits low-pressure liquid L feed from gas-liquid separator  10  to the shell side of isothermal liquid piston compressor  314 . Cooling liquid feed line  370  includes flow control valve  374 , which is operable to regulate the amount of low-pressure liquid passing into inlet head  362  of isothermal liquid piston compressor  314 . Liquid return line  372  permits returning low-pressure liquid L, which has a higher temperature than low-pressure liquid L in cooling liquid feed line  370  after thermal exchange within isothermal liquid piston compressor  314 , to flow from outlet head  364  back to gas-liquid separator  10 . Introducing the higher-temperature low-pressure liquid L back into gas-liquid separator  10  has the additional benefit of introducing heat into gas-liquid separator  10 , which drives the liquid and gas separation further. 
     The flow direction within the shell for production boost system  300  is “counter-current” in the sense that the low-pressure liquid L is introduced in an opposing flow direction (as shown in  FIG. 3  from top down) than the fluid and gas compression direction (as shown in  FIGS. 1-3  as bottom up) across several liquid piston compressor  360  tubes. The counter-current flow allows cooler low-pressure liquid L to contact the exterior of several liquid piston compressors  360  first, producing a greater temperature differential between the compressing gas within several liquid piston compressors  360  and the low-pressure liquid in shell fluid void  366 . 
     Production boost system  300  includes temperature controller  380  that is signally coupled to several portions of production boost system  300  for monitoring temperature conditions. In an embodiment of the system, production boost system includes a temperature controller that is operable to detect a temperature within the liquid piston compressor. Temperature controller  380  is in signal communication with several temperature probes and is operable to detect the temperatures of low-pressure gas G upstream of low-pressure gas inlet valve  16 , compressing gas within several liquid piston compressors  360  and cooling liquid feed upstream of flow control valve  374 . In an embodiment of the system, the temperature controller is also operable to selectively permit the introduction of a cooling liquid to the liquid piston compressor. Temperature controller  380  is in signal communication with flow control valve  374  and is operable to modify its position to achieve the appropriate cooling liquid feed flow. 
     Temperature controller  380  is operable to regulate the fluid flow rate of cooling liquid feed through shell fluid void  366  during the compression step such that an isothermal or as close to isothermal condition as feasible within several liquid piston compressors  360  occurs. In an embodiment of the method, the pressure boost system is operated such that the liquid piston compressor during the compression period is maintained in a substantially isothermal condition. In an embodiment of the method, the pressure boost system is operated such that the liquid piston compressor during the compression period is maintained in a significantly isothermal condition. In an embodiment of the method, the pressure boost system is operated such that the liquid piston compressor during the compression period is maintained in an isothermal condition.