Isothermal Compressor and Condenser Nozzles

Abstract

The present disclosure provides a novel configuration of a fluid pressurization nozzle, the mechanical design of which is relatively simple, for achieving an isothermal or quasi-isothermal pressurization process of a fluid, e.g., isothermal or quasi-isothermal compression of a gas. The fluid pressurization nozzle of the present disclosure utilizes the general principles of a diverging-converging nozzle (e.g., a Venturi nozzle), modified to eliminate or significantly attenuate the generation of shock waves within the nozzle, thereby facilitating efficient compression of the gas. The fluid pressurization nozzle of the present disclosure has a profile defining a cross-section that varies along its length. Thus, the fluid pressurization nozzle is configured to affect / manipulate the characteristics / physical properties of the fluid(s) propagating along it. Such physical properties may include, among others, pressure, Mach number, velocity, and temperature. Optionally, and preferably in some embodiments, the fluid compression nozzle of the present disclosure is configured to compress an suction fluid (e.g., a gas) introduced therein with the aid of a heat transfer liquid (HTL) propagating / flowing along it. The introduced suction fluid mixes with the HTL to form a liquid / gas mixture within which the gas is pressurized.

Description

[Technical Field]

[0001] FIELD OF THE DISCLOSURE The present disclosure relates generally to the field of pressurization devices, and more particularly to nozzles for pressurization of compressible fluids. [Background technology]

[0002] A conventional compression element for two-phase media flows can be, for example, a Venturi nozzle, a type of convergent-divergent passive compression device with no moving parts. Self-entraining Venturi nozzles operate on the same principle as conventional Venturi nozzles, but also include one or more gas inlets. They typically feature a convergent inlet section, a divergent outlet section, and possibly a constricted throat between them. Generally, Venturi nozzles use a high-speed, moving heat-transfer liquid (HTL) stream to entrain a nearly stationary, aspirated compressible fluid (e.g., gas). In a self-entraining Venturi nozzle, the driving stream accelerates by flowing through the convergent section, while its pressure drops above ambient pressure at the end of the convergent section, achieving maximum velocity at the nozzle throat. The high velocity of the HTL creates a region of low static pressure, resulting in a pressure difference between the HTL and the aspirated fluid at the nozzle throat. The pressure differential draws a suction fluid stream from the gas inlet(s) into the nozzle, where the suction stream and the driving stream mix to form a two-phase medium, typically at a converging throat section. A subsequent diverging section can increase the pressure of the gas / liquid mixture. Due to the high volumetric specific heat of the liquid, the pressure increase is isothermal or quasi-isothermal. Summary of the Invention [Problem to be solved by the invention]

[0003] However, in such nozzles, the flow velocity of the two-phase medium can easily reach supersonic speeds at high gas / liquid mixture flow rates, which can induce shock waves and reduce suction efficiency, output pressure, and overall efficiency.

[0004] There is a need in the art for fluid pressurization devices and techniques for efficient isothermal or quasi-isothermal pressurization of fluids and compression of gases, such as atmospheric or other gases. The devices and compression techniques described herein can provide very useful tools for increasing the efficiency, and potentially reducing the size, of fluid pressurization and other thermodynamic processes in energy conversion systems, particularly, but not limited to, heat engines (e.g., reaction turbines).

[0005] Generally, in a convergent-divergent nozzle such as a Venturi nozzle, the flow velocity of the two-phase medium can reach supersonic speeds at high airflow rates, which can induce shock waves and reduce suction efficiency, output pressure, and overall efficiency. [Means for solving the problem]

[0006] The present disclosure provides a novel configuration of a fluid pressurization nozzle that is relatively simple in its mechanical design for achieving an isothermal or quasi-isothermal pressurization process of a fluid, for example, isothermal or quasi-isothermal compression of a gas. The fluid pressurization nozzle of the present disclosure utilizes the general principles of a diverging-converging nozzle (e.g., a Venturi nozzle) modified to eliminate or significantly attenuate the generation of shock waves within the nozzle, thereby facilitating efficient compression of the gas.

[0007] Quasi-isothermal compression is understood as the pressurized suction fluid maintaining its temperature along the compression process, i.e., along the nozzle, in a range of not more than 110%, not more than 140%, or not more than 160% of its initial temperature in the process.

[0008] The fluid compression nozzle of the present disclosure has a profile that defines a cross-section that varies along its length. The fluid compression nozzle is therefore configured to affect / manipulate the properties of the fluid(s) propagating along it. Such properties may include pressure, Mach number, velocity, and temperature, among others. Optionally, and preferably in some embodiments, the fluid compression nozzle of the present disclosure is configured to compress an suction fluid (e.g., gas) introduced therein with the aid of a heat transfer liquid (HTL) propagating / flowing along it. The introduced suction fluid mixes with the HTL to form a liquid / gas mixture in which the gas is pressurized.

[0009] Optionally, and in some embodiments preferably, the suction fluid is a gas (such as air, nitrogen, hydrogen, an organic vapor, water vapor, or any other gas). Optionally, the suction fluid is a vapor (such as water vapor or an organic vapor). When the gas is introduced into the nozzle, it mixes with the HTL and is compressed to form a two-phase foam medium. The gas heats up as a result of the compression process. The HTL absorbs thermal energy from the gas during compression, thereby maintaining the gas at approximately the same temperature as the HTL during compression. The HTL temperature only increases slightly because the HTL has a relatively high heat capacity relative to the gas (which may be about 1000 times higher than the gas). This results in isothermal or quasi-isothermal compression of the gas. As a result, the compressed gas exits the nozzle at a pressure higher than ambient pressure. Optionally, when compressing a vapor, condensation occurs along with the compression. In some embodiments, the HTL enters the nozzle at an inlet pressure (which may be higher than ambient) and exits the nozzle at a pressure lower than the inlet pressure but higher than ambient pressure. Optionally, the outlet pressure is reduced by up to 30%. In some embodiments, the gas may be introduced at ambient pressure. Optionally, for a vapor, the vapor temperature is below the phase transition temperature, such that when mixed with a liquid, the gas changes phase and liquefies to form a pressurized liquid / HTL mixture, with at least one of the liquids in the mixture being pressurized. Optionally, the HTL is a vapor material in the liquid phase, and condenses after mixing to form a single pressurized liquid.

[0010] A fluid compression nozzle can be formed of multiple sections fluidly coupled to one another and defining a fluid flow path. In some embodiments, the gas compression nozzle includes an inlet section (also referred to as a "first fluid handling section"), a mixing section (also referred to as a "second fluid handling section"), an intermediate section (also referred to as a "third fluid handling section"), and an outlet section (also referred to as a "fourth fluid handling section"). The inlet section is adapted to accept a flow of HTL, possibly above ambient pressure and at subsonic speeds. The inlet section is shaped to initially depressurize the incoming HTL to below ambient pressure and accelerate it.

[0011] The mixing section is configured to introduce a compressible suction fluid (gas or vapor) therein and mix it with the reduced-pressure HTL, which is maintained at a substantially constant pressure, to form an HTL / fluid mixture. Optionally, and in some embodiments preferably, the suction fluid is a gas or vapor that mixes with the HTL flow to form a two-phase foam medium. The introduction of the gas or vapor is enabled by a pressure differential across the HTL in the mixing section that is lower than the pressure of the suction fluid. The foam medium slows the speed of sound below the speed of the two-phase mixture. The mixing section is shaped to achieve a supersonic flow velocity for the fluid mixture. The intermediate section is shaped to decelerate the fluid mixture to sonic or subsonic speeds while increasing the pressure of the fluid mixture.

[0012] The outlet section is configured to pressurize the fluid mixture (received from the mixing section) to a pressure higher than ambient pressure, and the flow in this section is subsonic. Due to the high heat capacity of the HTL, the mixture maintains quasi-isothermal compression. In some cases, the increase in pressure causes the gas phase (e.g., vapor) in the fluid mixture to condense into a liquid. Therefore, the outlet section is configured to discharge the fluid mixture, including the pressurized suction fluid, which can be a compressed gas or a pressurized liquid (in the case of condensation of a gas).

[0013] The present disclosure further provides a fluid pressurization system that can incorporate a fluid compression nozzle. Optionally, and in some embodiments preferably, the fluid compression system is configured to pressurize the suction fluid by repeatedly utilizing (reusing) the HTL. As described above, the HTL and suction fluid are mixed within the fluid pressurization nozzle, and a fluid mixture comprising the pressurized suction fluid (compressed gas) is discharged therefrom. The pressurized suction fluid, or a portion thereof, can then be separated from the mixture and released / discharged from the system to a designated pressurized fluid reservoir or for other use, while the HTL continues to circulate within the system for one or more additional fluid compression process(es).

[0014] To this end, in some embodiments, the gas compression system defines at least one closed-loop / circular flow path for the HTL. The fluid pressurization system includes a pump unit that pressurizes the HTL and directs the pressurized HTL into a compression nozzle disposed on the closed-loop flow path. The suction fluid can be introduced into the nozzle through one or more gas inlets located on the nozzle's peripheral envelope / sidewall or through a designated pipe / conduit. The fluid mixture (gas-liquid bubbly mixture) is released / discharged from the nozzle as the suction fluid is pressurized, or compressed if the suction fluid is gas. The HTL cools the suction fluid, but may slightly heat the suction fluid due to its much higher heat capacity. Optionally, and preferably in some embodiments, the fluid pressurization system is pressure-isolated from the surroundings. In this way, the pressurized fluid remains pressurized after being released from the nozzle.

[0015] The pressurized suction fluid can be separated from the discharged fluid mixture in a separate region / zone of the fluid pressurization system and discharged from the system, while the heated HTL continues to flow in a closed-loop path, being pressurized by a pump unit and then entering the nozzle. As described above, the HTL is discharged from the nozzle at a relatively low pressure differential, typically up to 30%, lower than the input pressure. In this way, a relatively small amount of energy can be used by the pump unit to pressurize the gas. The work generated by the quasi-isothermal compression plus the head loss in the nozzle reduces the outlet end stagnation pressure compared to the inlet starting stagnation pressure.

[0016] With each repetition / cycle, the temperature of the HTL increases (typically by one or a few degrees). The heated HTL can be used to generate energy, such as by high-temperature isothermal expansion of gas in a turbine. Optionally, the hot HTL can be replaced with a new, cooled HTL for continued operation of the gas compression system. Optionally, the HTL is cooled as it circulates through the isothermal compressor.

[0017] Thus, according to one broad aspect of the present disclosure, there is provided a nozzle for pressurizing a fluid, the nozzle including a nozzle inlet for receiving an HTL flow into the nozzle, an outlet, a suction fluid inlet, and an array of fluid-handling sections arranged in cascade fluid communication (series) to define a fluid flow path, the array including a first fluid-handling section downstream of or proximal to the nozzle inlet, the first fluid-handling section having a narrowing or converging configuration in the direction of the flow path to reduce the pressure of the incoming HTL below ambient pressure and accelerate the flow of the HTL flow. The narrowing or converging configuration should be understood as a structure having a decreasing cross-sectional area in the direction of the flow path, and the second fluid-handling section configured as a fluid mixer has an expanding configuration in the direction of the flow path. The expanding configuration should be understood as a structure having an increasing cross-sectional area in the direction of the flow path. The suction fluid inlet allows suction fluid communication between an ambient or compressed suction fluid source and the second fluid-handling section, and is configured to allow introduction of suction fluid into the second fluid-handling section to mix the suction fluid with the HTL, thereby obtaining an HTL / gas mixture, and the expanding configuration of the second fluid-handling section is designed to draw additional gas volume into the nozzle at a substantially constant pressure, at which stage the speed of sound decreases and the velocity of the mixture becomes supersonic. The nozzle has a third fluid manipulation section that narrows in the direction of the flow path to slow the supersonic flow of the fluid mixture received from the second fluid manipulation section to sonic or subsonic velocity and increase the pressure of the two-phase mixture flowing along the third fluid manipulation section; the fourth fluid manipulation section has a fourth fluid manipulation section that widens in the direction of the flow path and is configured to increase the pressure of the subsonic fluid mixture flow received from the third fluid manipulation section to a pressure above ambient pressure; and an outlet downstream of or defined by a distal end of the fourth fluid manipulation section for discharging the fluid mixture received from the fourth fluid manipulation section, the fluid mixture discharged from the outlet comprising the pressurized suction fluid.

[0018] In some embodiments, the HTL may include at least one of water, molten salt, thermal oil, ethylene glycol, molten metal, hydrocarbon liquid, antifreeze, liquefied gas, organic phase change liquid, pentane, propane, or any combination thereof.

[0019] In some embodiments, the suction fluid is a gas, which may include at least one of air, argon, CO2, hydrogen, natural gas, nitrogen, organic vapors, water vapor, or any combination thereof.

[0020] In some embodiments, the fluid mixture is a two-phase mixture and the pressurized suction fluid expelled from the outlet of the nozzle comprises a compressed gas.

[0021] In some embodiments, the suction fluid is a vapor that is condensed following quasi-isothermal compression, the fluid mixture discharged from the outlet is a liquid mixture, and the pressurized suction fluid discharged from the nozzle outlet comprises a pressurized liquid, i.e., the suction fluid is drawn into the nozzle in a vapor phase, changes phase to a liquid phase while flowing through the nozzle, and is discharged from the nozzle as a liquid.

[0022] In some embodiments, at least one of the fluid handling sections has a frustoconical longitudinal cross-sectional shape.

[0023] In some embodiments, the nozzle includes at least one conduit extending from its exterior into the second fluid handling section and configured to direct suction fluid into the mixing unit, allowing mixing of the suction fluid with the HTL flowing along the conduit.

[0024] In some embodiments, the at least one conduit is connectable to an external suction fluid source.

[0025] In some embodiments, the third fluid-handling section is configured to decelerate the fluid mixture flowing along the third fluid-handling section so that it reaches sonic or subsonic speeds at the tip or distal end of the third section.

[0026] In some embodiments, the discharged fluid mixture comprises a fluid having a discharge pressure value that is up to 1 bar, or up to 2 bar, or up to 0.5 bar, or up to 0.3 bar, or up to 0.1 bar lower than the initial pressure value of the HTL flowing into the first fluid handling section.

[0027] In some embodiments, the initial pressure value is up to 30% higher than the discharge pressure value.

[0028] In some embodiments, the suction fluid flowed into the first fluid handling section has a subsonic velocity.

[0029] In some embodiments, the nozzle inlet is configured to be in fluid communication with an HTL source to receive HTL at a pressure greater than ambient pressure.

[0030] According to another broad aspect of the present disclosure, there is provided an isothermal or quasi-isothermal fluid pressurization system including at least one nozzle of any one of the above-described embodiments of the nozzle or any combination thereof for receiving pressurized HTL pressurized to a pressure greater than ambient pressure from a nozzle inlet thereof, a fluid outlet, and a separation zone configured to receive the fluid mixture discharged from the at least one nozzle and separate the HTL and the pressurized suction fluid, wherein the pressurized suction fluid is directed to the fluid outlet and discharged from the fluid outlet to fill a tank with pressurized fluid or to direct the pressurized fluid to a pressurized fluid consumer.

[0031] In some embodiments, the fluid mixture ejected from the at least one nozzle is a two-phase mixture that includes a compressed gas.

[0032] In some embodiments, the fluid mixture ejected from the at least one nozzle is a liquid mixture comprising a pressurized liquid.

[0033] In some embodiments, the separation zone is configured to receive the fluid mixture ejected from the at least one nozzle and separate the HTL and the pressurized suction fluid, and the separated pressurized suction fluid is directed to and ejected from the fluid outlet.

[0034] In some embodiments of the system, the pressurized suction fluid is expelled from the fluid outlet at the same flow rate as the unpressurized fluid introduced into the nozzle.

[0035] In some embodiments, the fluid pressurization system includes a pump unit for increasing the pressure of the fluid received from the separation zone to obtain pressurized HTL and for forcing the pressurized HTL to flow to the nozzle.

[0036] In some embodiments, the pump unit is configured to receive fluid at a first pressure and increase the pressure to a second pressure that is higher than the first pressure.

[0037] In some embodiments, the pump unit is configured to receive fluid from the separation zone.

[0038] In some embodiments, the second pressure is at most 1 bar, or at most 2 bar, or at most 0.5 bar, or at most 0.3 bar, or at most 0.1 bar higher than the first pressure. The inlet pressure is optionally less than 30% higher than the outlet pressure.

[0039] In some embodiments, the second pressure is up to 30% higher than the first pressure.

[0040] In some embodiments, the pump unit comprises a vertical centrifugal pump.

[0041] In some embodiments, the vertical centrifugal pump has a bottom fluid inlet configured to allow liquid to enter, the liquid inlet being in fluid communication with a liquid drain of a separation zone that stores separation liquid.

[0042] In some embodiments, the vertical centrifugal pump has at least one arm supporting a fluid flow therealong, the at least one arm being fluidly coupled to at least one nozzle.

[0043] In some embodiments, the vertical centrifugal pump is rotatable about its vertical axis, thereby allowing for the aspiration of HTL through the bottom fluid inlet.

[0044] In some embodiments, the HTL flows through a fluid flow path in the system, the fluid flow path comprising at least one closed loop flow path, i.e., the separated liquid in the separation zone is pumped back to the nozzle, and the pump unit is configured to receive and pressurize fluid from the separation zone, thereby obtaining pressurized HTL, and to flow it through at least one nozzle.

[0045] In some embodiments, the closed loop flow path is pressure isolated from the environment, ie, the pressure within the pump, nozzle, and separation zone is isolated from ambient pressure.

[0046] In some embodiments, the aspirating fluid is separated from the two-phase mixture in the separation zone by gravity.

[0047] In some embodiments, the separation zone comprises a curved or circular frame onto which the two-phase mixture is discharged from the nozzle, and contact of the mixture with the curved or circular frame results in film flow on the surface of the curved or circular frame, thereby separating the gas from the liquid.

[0048] In some embodiments, the fluid outlet includes a pressure regulating valve configured to controllably flow the compressed fluid through the fluid outlet in response to either (i) a positive pressure differential between the compressed fluid and a fluid tank fluidly coupled to the fluid outlet, or (ii) exceeding a pressure threshold of the compressed fluid.

[0049] In some embodiments, the fluid pressurization system includes a heat exchanger configured to receive a portion of the HTL from the separation zone, i.e., the HTL separated from the suction fluid, and transfer excess heat generated by compression and by friction from the flow of liquid within the system to an external heat consumer or sink, and the HTL returns to the separation zone after passing through the heat exchanger.

[0050] In some embodiments, the fluid pressurization system includes a temperature sensor for sensing the temperature of the liquid in the separation zone and generating data indicative of the temperature of the liquid, a liquid valve configured to controllably release the liquid toward the heat exchanger, and a controller configured to (i) receive the temperature data and (ii) controllably open the liquid valve when the temperature exceeds a selected threshold.

[0051] According to yet another broad aspect of the present disclosure, a method for pressurizing a fluid includes the steps of: (i) increasing the pressure of an HTL from a first pressure to a second pressure; (ii) reducing the pressure of the HTL from the second pressure to below ambient pressure while accelerating the HTL; and (iii) allowing an aspiration fluid at ambient pressure, the aspiration fluid from an ambient or near ambient pressure closed system to flow into the liquid while maintaining the aspiration fluid at about the second pressure and ultrasonically pressurizing the liquid. (iv) narrowing the flow path of the mixture to increase its pressure and reduce its velocity to less than supersonic speed (the speed of sound of the mixture is reduced below the velocity of the mixture during mixing of the gas and liquid); (v) widening the flow path of the mixture to increase its pressure to a third pressure above the initial suction fluid pressure while further reducing its velocity; and (vi) separating pressurized suction fluid from the fluid mixture and directing it to a pressurized suction fluid reservoir.

[0052] In some embodiments, step (ii) comprises gradually narrowing the flow path of the HTL.

[0053] In some embodiments, step (iii) comprises gradually widening the flow path of the fluid mixture.

[0054] In some embodiments, mixing the HTL flow with an aspirating fluid comprises introducing an aspirating fluid from an external fluid source.

[0055] In some embodiments, the separating step comprises gravity separation.

[0056] In some embodiments, the separating step comprises directing the released mixture onto a curved surface.

[0057] In some embodiments, step (i) comprises pumping the liquid through an increasingly narrowing flow path to effect step (ii).

[0058] In some embodiments, the method further comprises separating the aspirated fluid from the two-phase mixture.

[0059] For a better understanding of the subject matter disclosed herein, and to illustrate how it may be carried out in practice, embodiments will now be described, by way of non-limiting example only, with reference to the accompanying drawings, in which: [Brief explanation of the drawings]

[0060] [Figure 1] 1A and 1B are schematic diagrams of non-limiting examples of nozzles for pressurizing fluids according to one embodiment of the present disclosure. [Figure 2] 2A and 2B are schematic diagrams of fluid pressurization systems according to some possible embodiments of the present disclosure, where FIG. 2A illustrates a fluid pressurization system with a closed-loop cavity and FIG. 2B illustrates a fluid pressurization system including a vertical centrifugal pump. [Figure 3] FIG. 1 shows the experimental installation of the nozzle. DETAILED DESCRIPTION OF THE INVENTION

[0061] One or more specific and / or alternative embodiments of the present disclosure will now be described with reference to the drawings, which are to be considered in all respects only as illustrative and not in any way restrictive. It will be apparent to those skilled in the art that the present invention may be practiced without such specific details. In an effort to concisely describe these embodiments, not all features or details of an actual implementation are described in detail herein. Elements shown in the drawings are not necessarily to scale or in precise proportion, but this is not critical. Rather, emphasis is placed on clearly illustrating the principles of the present invention so that those skilled in the art can make and use the interface device after understanding its features. The present invention may be provided in other specific forms and embodiments without departing from the essential characteristics described herein.

[0062] With regard to an overview of some exemplary features, process steps, and principles of the present invention, the example instrumentation shown generally and diagrammatically in the figures is not intended for fluid pressurization. These fluid pressurization devices are shown as one exemplary embodiment illustrating many of the features, processes, and principles used to provide isothermal or quasi-isothermal compression and pressurization processes, but they are useful in other applications and may be made in different variations. Accordingly, this description will proceed with reference to the examples shown, but with the understanding that once the principles are understood from the description, teachings, and drawings herein, the invention as claimed below may be implemented in countless other ways. All such variations, as well as any other modifications that are obvious to those skilled in the art and useful in minimally invasive applications, may be suitably employed and are intended to be within the scope of this disclosure.

[0063] Reference is now made to FIGS. 1A and 1B, which illustrate cross-sectional views of a non-limiting example of a nozzle according to one embodiment of the present disclosure. FIG. 1A illustrates a nozzle 10 constructed in accordance with the principles of the present disclosure for isothermal or quasi-isothermal pressurization of a fluid. The nozzle 10 is formed by an array 12 of fluid-handling sections. In this non-limiting example, the gas compression nozzle 10 includes a first fluid-handling section 12f, a second fluid-handling section 12s, a third fluid-handling section 12t, and a fourth fluid-handling section 12r, respectively. As shown in FIG. 1, the nozzle 10 has a body 13 that defines a perimeter of the nozzle 10, such that the fluid-handling sections 12f, 12s, 12t, and 12r are fluidly connected / coupled to one another to form an integral structure.

[0064] As shown in FIG. 1 , the fluid manipulation sections are arranged in a cascade along a common longitudinal axis O, whereby the fluid manipulation sections are in fluid communication with one another and define a flow path for the fluid propagating / flowing along the nozzle 10. In some embodiments, the nozzle 10 includes a nozzle inlet 14i and a nozzle outlet 14u, thereby forming a flow path in direction L. The nozzle inlet 14i is generally located upstream of the first manipulation section 12f or is defined by its proximal tip / end and may be adapted to receive a liquid flow into the nozzle 10. In some embodiments, the nozzle inlet 14i is in fluid communication with a drive / actuation fluid source (not shown) containing a liquid pressurized to a pressure greater than ambient pressure. The nozzle inlet 14i is adapted to receive pressurized HTL from a pump (not shown). Optionally, and in some embodiments preferably, the HTL may include, among other things, water, molten salt, thermal oil, ethylene glycol, molten metal, hydrocarbon liquid, antifreeze, liquefied gas, or any combination thereof.

[0065] The nozzle outlet 14u may generally be located downstream of or may be defined by the distal tip / end of the fourth operating section 12f and is configured to discharge pressurized fluid from the gas compression nozzle 10.

[0066] In some embodiments, the first fluid-handling section 12f has a narrowing / converging configuration in the flow path direction L. Thus, the first fluid-handling section 12f is configured to reduce the pressure of the HTL flowed therein to below ambient pressure and accelerate the flow of the HTL stream. The HTL is then pumped to an initial pressure P, which may be higher than ambient pressure. i , and an initial velocity v, which may be subsonic (Mach number M<1). i As the HTL propagates / flows through the first fluid handling section 12f, it increases in velocity while experiencing a pressure P f (P f <P i ) is reduced in pressure.

[0067] The second fluid manipulation section 12s is disposed downstream of the first fluid manipulation section 12f and receives the HTL from the first fluid manipulation section 12f. In some embodiments, the second fluid manipulation section 12s is configured to operate as a fluid mixer to introduce / entrain a suction fluid that is mixed with the HTL received from the first fluid manipulation section 12f, thereby obtaining a fluid mixture. The pressure within section 12s is lower than the pressure of the incoming suction fluid, thereby causing suction of the suction fluid. Optionally, and in some embodiments preferably, the suction fluid is a material gas that is drawn / entrained into the nozzle due to the pressure difference between the HTL (which is at a pressure below ambient) and the gas (which is at a pressure above ambient pressure) within the second fluid manipulation section 12s. Upon suction of the gas, the gas mixes with the HTL (e.g., HTL) to obtain a two-phase mixture, typically a foamy mixture / medium. As a result, the speed of sound decreases, and the flow of the mixture becomes supersonic.

[0068] To that end, as shown in FIG. 1 , the second fluid-handling section 12s may be provided with one or more suction fluid inlets 16i (e.g., through-holes and / or openings) configured to allow suction fluid to be entrained / drawn into the fluid-handling section 12s for mixing with the liquid. Alternatively, or additionally, as shown, the nozzle 10 may be associated with a pipe / conduit 16p extending from its exterior into the second fluid-handling section 12s. The conduit 16p is configured to direct the suction fluid into the mixing unit and allow mixing with the HTL flowing along it. In some embodiments, the one or more gas inlets 16i and / or conduit 16p are further configured to allow fluid communication between the second fluid-handling section 12s and a suction fluid source (not shown) and / or the ambient environment.

[0069] In some embodiments, the second fluid-handling section 12s has a configuration that expands / diverges in the flow path direction L to facilitate the injection of the aspirating fluid while maintaining the flow at a substantially constant pressure. Additionally, the foam medium causes the sonic velocity of the two-phase mixture to decrease below the flow velocity of the two-phase mixture, thereby causing the two-phase mixture to flow at supersonic velocities (Mach number M<1).

[0070] The third fluid manipulation section 12t is disposed downstream from the second fluid manipulation section 12s and receives the fluid mixture from the second fluid manipulation section 12s. In some embodiments, the third fluid manipulation section 12t has a narrowing / converging configuration in the flow path direction L to slow the flow of the fluid mixture received from the second fluid manipulation section 12s to sonic (M=1) or subsonic (M>1) speeds, possibly at the tip / distal end of the third fluid manipulation section 12t, and to increase the pressure of the fluid mixture flowing along the third fluid manipulation section 12t.

[0071] The fourth fluid manipulation section 12r is disposed downstream of the third fluid manipulation section 12t and receives the fluid mixture from the third fluid manipulation section 12t at subsonic speed, terminating in this non-limiting example at a nozzle outlet 14u. In some embodiments, the fourth fluid manipulation section 12r has a configuration that expands in the flow path direction L. Thus, the fourth fluid manipulation section 12r is configured to increase the pressure of the fluid mixture received from the third fluid manipulation section 12t to a pressure higher than ambient pressure. The fluid mixture comprises pressurized suction fluid as it is discharged from the nozzle outlet 14u.

[0072] As described above, the fluid mixture can be a two-phase mixture of HTL and gas or HTL and vapor. The HTL acts as a cooling medium thermally coupled with the gas, absorbing heat / thermal energy generated as a result of the compression process and resulting in cooling of the gas, while the HTL is only slightly heated, thereby achieving isothermal or quasi-isothermal compression of the gas. Thus, at the tip / distal end of the fourth fluid manipulation section 12r, the two-phase mixture includes compressed gas and heated liquid (HTL) and can be discharged through the nozzle outlet 14u. In some embodiments, the vapor condenses into liquid due to the increase in pressure, resulting in the liquid mixture being discharged from the nozzle outlet 14u, and thus the liquid mixture includes pressurized liquid. In some embodiments, the discharged fluid mixture is discharged at the initial pressure P of the HTL flowed to the first fluid manipulation section 12f. i Discharge pressure P up to 0.1 bar to 5 bar or up to 30% lower than dis (P dis <P i Optionally, the outlet of the nozzle is flow-connected to the inlet of the nozzle via a mixture separation section and a circulation pump.

[0073] The terms "narrowing" and "converging" are used herein to indicate that the cross section of the fluid flow (transverse to direction L) decreases in that direction, and the terms "diverging" and "diverging" are used herein to indicate that the cross section of the fluid flow increases in that direction.

[0074] Figure IB shows a two-phase "reverse Laval" nozzle configured to isothermally compress a gas by increasing its pressure and mixing it with an HTL. Note that the figure is not to scale.

[0075] An HTL, such as water, a low-freezing-point liquid, a hydrocarbon liquid, and / or other stream in the nozzle, enters the inlet at a pressure higher than ambient and exits the outlet at a pressure higher than ambient. A gas, such as air, hydrogen, or any other gas, is drawn into the HTL, compressed, cooled by the HTL, and exits the outlet at a pressure higher than ambient. While FIG. 1B shows an example of water as the HTL and air as the gas, it should be noted that the HTL may be selected from any suitable HTL, and the gas may be any suitable gas that is compressed. Optionally, the HTL initial pressure and speed are generated by a pump. Optionally, the initial and final pressure values ​​of the HTL are identical to within 10%. Optionally, the initial and final pressures of the HTL are identical to within 20% or 30%.

[0076] The operating temperature of the HTL is preferably as low as possible. Optionally, it is below 100°C, 25°C, 15°C, or 0°C. Optionally, for a low-freezing-point HTL, the operating temperature is below −10°C, −25°C, or −50°C. Optionally, the HTL temperature is below −195°C when the HTL is liquid nitrogen, or below 4.2K when the HTL is liquid helium.

[0077] Optionally, such compressors can be used in a cascade configuration to reach higher pressures. For the second pressure stage, compressed gas is introduced into the gas supply of a second closed-loop compressor. For example, the first stage compresses air to 15 bar using water as the HTL and a supersonic nozzle. This compressed air then flows into a second supersonic nozzle in a second closed-loop compressor, which maintains the pressure at 30 bar. At the nozzle, the pressure drops below 15 bar, allowing the air to enter the nozzle. At the nozzle exit, the pressure rises to 30 bar, and the air is compressed while being cooled by water.

[0078] As shown in FIG. 1B, the nozzle may include the following sections, in order: (1) A converging inlet section consisting of only HTL (e.g., water) to reduce the pressure above ambient pressure. (2) A diverging two-phase flow section where pressure is maintained constant while air is drawn into the HTL from the surroundings through holes, air inlets, or voids in the nozzle envelope. The section marked with a "-" is where the suction begins, and the section marked with a "+" is where the suction ends. The mixture reduces the sonic velocity below the velocity of the mixture. At the end of the "diverging two-phase flow section" (marked with a "+"), the flow is supersonic. (3) A converging two-phase section where the pressure of the mixture increases and the Mach number (ratio of flow velocity to the speed of sound) decreases. At the end of this section (marked with an "*"), Mach = 1. Optionally, Mach-1 is achieved with a constricting / converging section. (4) A diverging two-phase outlet where the mixture pressure increases and the Mach number decreases. At the end of this section, the mixture reaches its maximum pressure (as the HTL itself has a higher pressure when introduced into the nozzle).

[0079] 2A and 2B, there are schematic diagrams of non-limiting examples of isothermal fluid pressurization systems 200 according to some possible embodiments of the present disclosure. In some embodiments, gas compression system 200 is configured and operable to compress gas by repeatedly utilizing (recirculating) an HTL, such as an HTL flowing / propagating within a fluid flow path that includes at least one closed-loop flow path as described in further detail below.

[0080] FIG. 2A illustrates a closed-loop flow of heat transfer liquid (HTL), such as water, antifreeze, thermal oil, or any other liquid, driven at above-ambient pressure by a pump 208 to form a gas pressurization system 200. The pump has a high pressure at its inlet and a higher pressure at its outlet. The pumping action generates flow and compensates for pressure losses due to compression work and head loss. The gas pressurization system 200 includes at least one nozzle 10 configured as described in FIGS. 1A and 1B to receive the above-ambient pressure HTL from a nozzle inlet 14i. The system 200 includes a separation zone / region 204 fluidly coupled downstream of the nozzle outlet 14u such that the nozzle 10 and the separation zone / region 204 define a closed-loop liquid flow path L1. As described above with reference to FIGS. 1A and 1B, the at least one nozzle 10 provides a fluid mixture including a pressurized suction fluid (compressed gas or pressurized liquid) and the HTL. The pressure of the mixture, and therefore the HTL, at the outlet of the nozzle 10 drops only slightly, e.g., at most 1%, 2%, or 10%, relative to the pressure of the HTL at the inlet of the nozzle 10. In this regard, it should be noted that the separation zone / region 204 creates a pressure isolation environment within the system. In this manner, the pressurized suction fluid being discharged from the nozzle 10 is maintained under pressure as it propagates through the separation zone / region 204.

[0081] The suction fluid (preferably, a gas) to be compressed may be flowed to the nozzle 10 via one or more fluid inlets 16i formed by through-holes, holes, air inlets, or voids, and / or at least one suction fluid supply means, such as a pipe / conduit 16p extending from outside the system 200 into the second fluid-handling section 12s. The suction fluid supply means is in fluid communication with the nozzle 10 and is configured to flow the suction fluid into the second fluid-handling section 12s of the nozzle 10, where the pressure of the HTL is reduced below the pressure of the suction fluid (e.g., gas) to enable mixing of the suction fluid with the HTL flowing along the nozzle 10. To this end, the system 200 may be associated with one or more gas sources (not shown) fluidically coupled to the one or more fluid inlets 16i and / or the pipe / conduit 16p.

[0082] The separation zone / region 204 is configured to receive the fluid mixture, including the pressurized suction fluid, being discharged from at least one nozzle 10 and separate the pressurized suction fluid from the fluid mixture (i.e., separate the pressurized suction fluid from the HTL). The pressurized suction fluid can be a compressed gas or a pressurized liquid. In embodiments in which the suction fluid is discharged from the nozzle in a liquid phase, the suction fluid can be aspirated in a gas phase and change phase while flowing through the nozzle, particularly in the fourth operating section, or can be aspirated in a liquid phase and maintain that phase while flowing through the nozzle. The pressurized suction fluid is directed to and discharged from the gas outlet 206. Optionally, and preferably in some embodiments, the gas outlet 206 includes a pressure regulator valve 206v that can be selectively / controllably operable to flow the pressurized suction fluid through the gas outlet 206 when there is a positive pressure differential between the pressurized suction fluid and a suction fluid tank 210 fluidly coupled to the gas outlet 206, or when a pressure threshold for the pressurized suction fluid is exceeded.

[0083] In some embodiments, the HTL is a liquid vapor suction fluid. In such cases, the HTL is maintained as a liquid in the low-pressure mixing section due to the high velocity and short duration in the mixing section. In such cases, the vapor is optionally condensed, and a single-phase flow emerges from the outlet. This optionally eliminates the need for a separation section. The outlet pipe extracts compressed fluid from the compressor at a mass velocity approximately equal to the suction mass velocity.

[0084] In some embodiments, system 200 may include or be associated with a heat exchanger 212 in fluid communication with separation zone / region 204. Heat exchanger 212 is configured to receive a portion of the HTL separated from the pressurized suction fluid from the separation zone to transfer excess heat (which may be generated by friction from the flow of liquid within the system) to an external heat sink or heat sink (not shown). To that end, system 200 may include a temperature sensor (not shown) housed in separation zone / region 204 and configured to generate data indicative of the temperature of the portion of the HTL received in separation zone / region 204. The data may be transmitted to a controller (not shown) configured to process the data and use it to operate valve 204v, i.e., controllably open or close the valve, when the temperature of the HTL exceeds a selected threshold. Valve 204v is configured to controllably release the HTL from separation zone / region 204 toward heat exchanger 212. Once the HTL has cooled, it is directed back to the separation zone for return to system 200.

[0085] It should be noted that in some embodiments, the heat exchange between the HTL and the environment is sufficient to remove excess heat, and therefore a heat exchanger is not required.

[0086] The system 200 also includes a pump unit 208 disposed in the fluid flow path L1. The pump unit 208 is configured to increase the pressure of the HTL received from the separation zone / region 204, thereby obtaining pressurized HTL, and to force the pressurized HTL into the gas nozzle 10 to undergo another cycle.

[0087] Thus, during operation, the pressurized HTL (HTL) can continuously circulate / flow along the closed-loop liquid flow path L1 and can be repeatedly utilized for pressurization of suction fluid within the system 200. With each repetition / cycle of the HTL, the HTL can be heated by the gas compression / compression process within the nozzle 10. Upon reaching a selected temperature threshold, the heated HTL can be replaced with a cooled HTL, while the heated HTL can be used for other purposes, such as high-temperature isothermal expansion of air within a turbine.

[0088] In the non-limiting example of FIG. 2B , the pressurization system 200 operates by rotating a nozzle while simultaneously supplying HTL to the nozzle at the inlet and gas to the mixing chamber through the rotating arm. Centrifugal force drives the HTL flow. The nozzle is similar to the nozzles described in FIGS. 1A and 1B , and gas is drawn into the rotating nozzle in their mixing chamber. The nozzle includes a narrow section where the pressure is reduced below ambient pressure. Air is drawn into the nozzle in this narrow section and mixed with the HTL. The gas exiting the nozzle is compressed and cooled by the HTL. The entire rotating nozzle is placed inside a sealed chamber with a pressure valve for releasing the compressed air at a constant flow rate. The fluid pressurization system 200 includes a chamber 240 defining a pressure isolation compartment with an internal pressure isolation environment. The pump unit is configured as a vertical centrifugal pump 220 for pumping fluid and supporting the internal fluid flow. The vertical centrifugal pump 220 is rotatable about its vertical axis X, such that centrifugal force can draw liquid through the bottom fluid inlet. In some embodiments, the vertical centrifugal pump 220 is formed by a rotatable suction member 220p disposed substantially perpendicular to the bottom surface of the chamber 240. The rotatable suction member 220p has an intake port at its bottom that is suspended above the bottom surface of the chamber 240 and can be submerged in the fluid drain 260.

[0089] 1A and 1B. In this example, the vertical centrifugal pump 220 is fluidly coupled to a first nozzle 10a and a second nozzle 10b via a first arm 220a and a second arm 220b, respectively. The first arm 220a and the second arm 220b are fluidly coupled to a rotatable suction member 220p and configured to assist fluid flow along the suction member 220p and direct the fluid toward the nozzles 10a and 10b, respectively.

[0090] The gas to be compressed is supplied to the nozzles 10a, 10b via channel 220g, which extends from outside the gas pressurization system 200 and along first arm 220a and second arm 220b into the second fluid-handling section (12s in FIG. 1A) of each of the nozzles 10a, 10b. The compressed gas is separated from the liquid by gravity as the two-phase mixture is discharged from each of the nozzles 10a, 10b, such that the liquid is drawn by gravity to a liquid drain 260 at the bottom of the chamber 240, while the compressed gas propagates to the upper section of the chamber 240 to be released through one or more gas outlets located at the top of the chamber 240 (one such gas outlet 206 is shown in FIG. 2B). In this manner, the system 200 defines multiple closed-loop flow paths for the HTL; in this example, two closed-loop flow paths associated with the nozzles 10a, 10b are shown.

[0091] In this non-limiting example, the heat exchanger 212 may be in fluid communication with the liquid drain 260 to receive a portion of the liquid separated from the compressed gas and to transfer excess heat (which may be generated by friction from the flow of liquid within the system) to an external heat consumer (not shown). As mentioned above, in some embodiments, the heat exchanger 212 is not required because the HTL exchanges heat with the surroundings at a sufficient rate.

[0092] Another example is compressing and condensing an organic vapor, such as pentane, for an organic Rankine cycle (ORC). Optionally, the liquid pentane is HTL, and the vapor pentane is compressed and condensed by a compressor / condenser. In this example, the liquid pentane exits the compressor without the need for a mixture separation zone. Experimental data

[0093] An exemplary setup of the nozzle was constructed to test the efficiency of a compressor.

[0094] The efficiency is the ratio of ideal isothermal compression to the power input by the pump (excluding the pump efficiency).

number

[0095] The water flow in the nozzle is 48.4 m 3 / Hr (approximately 13.5 liters / sec). The measured inlet pressure is 8.35 bar and the measured outlet pressure is 6.5 bar. Air is sucked into the nozzle and compressed. In the wide section of pipe, the air separates and leaves the flow meter at a flow rate of 6.5 liters / sec and 6.5 bar (instead of 7.2 bar in an ideal system). We demonstrate the following efficiencies:

number

[0096] This inefficiency is the result of head loss in the nozzle. In these small capacity compressor demonstrations, the nozzle diameter is about 2 inches, which is a significant head loss. By increasing the flow rate by a factor of 10, the nozzle diameter is reduced by 500 m. 3 / hr water and 650 liters / sec air, head loss is expected to decrease dramatically and the expected isothermal efficiency is TIFF2025531174000004.tif exceeds 625.

[0097] Throughout this application, the term "about" should be interpreted as ±20% of the nominal value. For example, if a value is about 10, it should be understood to be in the range of 8 to 12.

Claims

1. A nozzle for pressurizing a compressible fluid, the nozzle comprising a nozzle inlet, an outlet, a suction fluid inlet, and an array of fluid handling sections arranged in a cascade configuration to define the fluid path, the nozzle being in fluid communication with a heat conduction liquid (HTL) source to receive a flow of HTL into the nozzle at a pressure higher than the ambient pressure. The aforementioned array is, A mixing section having a configuration that expands in the direction of the flow path to receive the heat transfer liquid at a pressure lower than the ambient pressure or lower than the pressure of the suction fluid in the suction fluid source, wherein the suction fluid inlet is configured to allow the suction fluid to be introduced into the mixing section to mix with the heat transfer liquid to obtain a two-phase fluid mixture, the mixing reducing the sound velocity of the two-phase fluid mixture to less than the flow velocity of the two-phase fluid mixture flowing through the mixing section, thereby making the two-phase mixture flow supersonic at least the distal end of the mixing section, An intermediate section having a shape that narrows in the direction of the flow path in order to slow the flow of the fluid mixture received from the mixing section to the speed of sound or subsonic speed and to increase the pressure of the two-phase mixture flowing along the intermediate section, An outlet section having a shape that expands in the direction of the flow path and configured to raise the pressure of the fluid mixture received from the intermediate section to a pressure higher than the ambient pressure, Includes, The nozzle has an outlet located downstream of the outlet section or formed by its distal end, for discharging a fluid mixture received from the outlet section, the fluid mixture discharged from the outlet containing a pressurized suction fluid.

2. The nozzle according to claim 1, comprising a first fluid handling section located downstream of the nozzle inlet and upstream of the mixing section, or the proximal end thereof constituting the nozzle inlet, and having a configuration that narrows in the direction of the flow path to reduce the pressure of the heat transfer liquid flowing therein to below the ambient pressure or below the pressure of the suction fluid in the suction fluid source, and to accelerate the flow of the heat transfer liquid.

3. The nozzle according to claim 1, wherein the heat transfer liquid comprises at least one of water, molten salt, heat transfer oil, ethylene glycol, molten metal, hydrocarbon liquid, antifreeze, liquefied gas, or any combination thereof.

4. The aforementioned suction fluid is a gas or vapor, The nozzle according to any one of claims 1 to 3, wherein the gas comprises at least one of air, argon, CO2, hydrogen, natural gas, nitrogen, organic vapor, water vapor, or any combination thereof.

5. The nozzle according to claim 1, wherein the fluid mixture is a two-phase mixture, and the pressurized suction fluid discharged from the outlet of the nozzle contains compressed gas.

6. The nozzle according to claim 1, wherein the fluid mixture discharged from the outlet is a liquid mixture, and the pressurized suction fluid discharged from the nozzle outlet includes a pressurized liquid.

7. The nozzle according to claim 1, wherein the nozzle includes at least one conduit extending from outside the nozzle into the mixing section, the conduit being configured to enable mixing of the suction fluid and the HTL flowing along the conduit, and to guide the suction fluid into the mixing section to reduce the sound velocity of the mixture to less than the velocity of a mixture having a supersonic flow.

8. The nozzle according to claim 7, wherein the at least one conduit is connectable to an external suction fluid source.

9. The nozzle according to claim 1, wherein the intermediate section is configured to decelerate a fluid mixture flowing along the intermediate section so that it reaches the speed of sound or subsonic speed at the tip of the intermediate section.

10. The discharged fluid mixture includes a fluid having a discharge pressure value up to 1 bar lower than the initial pressure value of the heat transfer liquid flowing to the first fluid operation section. The nozzle according to claim 1, wherein the initial pressure value is up to 30% higher than the discharge pressure value.

11. The nozzle according to claim 1, wherein the suction fluid flowing to the first fluid operation section has a subsonic velocity.

12. The nozzle according to claim 1, wherein the heat transfer fluid and the suction fluid are made of the same material.

13. A fluid pressurization system, A nozzle according to claim 1 for receiving a pressurized heat transfer liquid pressurized to a pressure higher than the ambient pressure from the nozzle inlet, Fluid outlet and A separation zone configured to receive a fluid mixture discharged from at least one nozzle and separate a heat transfer liquid from a pressurized suction fluid, wherein the pressurized suction fluid is directed toward the fluid outlet and discharged through the fluid outlet, A fluid pressurization system, including

14. The fluid pressurization system according to claim 13, wherein the separation zone is configured to receive a fluid mixture discharged from at least one nozzle and separate the heat transfer liquid from the pressurized suction fluid, and the separated pressurized suction fluid is directed toward the fluid outlet and discharged through the fluid outlet.

15. The fluid pressurization system according to claim 13, further comprising a pump unit for increasing the pressure of the fluid received from the separation zone to obtain the pressurized heat transfer liquid, and for flowing the pressurized heat transfer liquid to the nozzle.

16. The fluid pressurization system according to claim 15, wherein the pump unit is configured to receive the fluid at a first pressure and raise its pressure to a second pressure higher than the first pressure.

17. The fluid pressurization system according to claim 15, wherein the pump unit is configured to receive the fluid from the separation zone.

18. The second pressure is up to 3 bar higher than the first pressure. The pump unit includes a vertical centrifugal pump, The vertical centrifugal pump has a bottom fluid inlet configured to allow the flow of liquid through it, the fluid inlet is in fluid communication with the liquid drain of the separation zone, the separation zone stores the separated liquid, The vertical centrifugal pump has at least one arm, the arm assists the fluid flow along the arm and is fluid-coupled to at least one nozzle. The fluid pressurization system according to claim 17, wherein the vertical centrifugal pump is rotatable about its vertical axis, thereby enabling the suction of the heat transfer liquid through the bottom fluid inlet.

19. The heat transfer fluid flows through a fluid channel in the system, the fluid channel includes at least one closed-loop channel, and the pump unit is configured to receive the fluid from the separation zone, pressurize it, thereby obtaining the pressurized heat transfer fluid, and flow it to at least one nozzle. The fluid pressurization system according to claim 13, wherein the closed-loop channel is pressure-isolated from the environment.

20. The fluid pressurization system according to claim 13, wherein the fluid outlet includes a pressure regulating valve configured to control the flow of the compressed fluid through the fluid outlet in response to either (i) a positive pressure difference between the compressed fluid and a fluid tank fluid-coupled to the fluid outlet, or (ii) the compressed fluid exceeding a pressure threshold.

21. The fluid pressurization system according to claim 13, comprising a heat exchanger configured to receive a portion of the heat transfer liquid from the separation zone and transfer excess heat to an external heat consumer, wherein the heat transfer liquid returns to the separation zone after passing through the heat exchanger.

22. A temperature sensor for sensing the temperature of the liquid in the separation zone and generating data indicating the temperature of the liquid, A liquid valve configured to controllably discharge liquid toward the heat exchanger, (i) A controller configured to receive the temperature data and (ii) to controllably open the liquid valve when the temperature exceeds a selected threshold, The fluid pressurization system according to claim 13, including the above.

23. A method for pressurizing a fluid, the method comprising the following series: (i) A step of increasing the pressure of the heat transfer liquid from a first pressure to a second pressure, (ii) A step of accelerating the heat transfer liquid while reducing the pressure of the heat transfer liquid from the second pressure to below the ambient pressure, (iii) A step of introducing an suction fluid having an initial pressure which is the ambient pressure into the heat transfer liquid while maintaining it at approximately the second pressure, thereby obtaining a fluid mixture at approximately the second pressure and supersonic speed, (iv) The steps of narrowing the flow path of the fluid mixture to increase the pressure of the mixture and reduce the velocity of the mixture to less than supersonic, (v) The steps of expanding the flow path of the mixture to raise the pressure of the mixture to a third pressure higher than the initial suction fluid pressure, and at the same time further reducing the velocity of the mixture, (vi) Separating the heat transfer liquid from the pressurized suction fluid by gravity, separating the pressurized suction fluid from the fluid mixture and directing the pressurized suction fluid to the pressurized suction fluid storage section, Methods that include...

24. The method according to claim 23, wherein step (ii) includes gradually narrowing the flow path of the heat transfer liquid.

25. The method according to claim 23, wherein step (iii) comprises gradually expanding the flow path of the fluid mixture.

26. The heat transfer liquid comprises at least one of water, hydrocarbon liquid, antifreeze, and liquefied gas. The method according to claim 23, wherein the gas comprises at least one of air, hydrogen, natural gas, and nitrogen.

27. The method according to claim 23, wherein the step of mixing the heat transfer liquid flow with the suction fluid includes the step of introducing the suction fluid from an external fluid source.

28. The method according to claim 23, wherein the separation step includes the step of directing the released mixture onto a curved surface.

29. The method according to claim 23, wherein step (i) includes the step of dispensing a liquid and directing the liquid toward a gradually narrowing channel in order to carry out step (ii).

30. The method according to claim 23, further comprising the steps of separating a gas from the two-phase mixture and discharging the two-phase mixture through the gradually narrowing channel.

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