Recirculating flash vessel structures

Abstract

Systems, methods, and apparatuses for producing high-pressure steam are provided. A compressor train includes a series of at least two compressors, and inlet, and an outlet providing high-pressure steam. A flash vessel structure includes a series of at least two flash vessels, a terminal flash vessel at one end of the flash vessel structure, and a vapor outlet of the terminal flash vessel fluidly coupled to the inlet of the compressor train. Vapor outlets of a remainder of the series of at least two flash vessels are fluidly coupled between compressors of the series of at least two compressors. A steam recirculation manifold includes a vapor inlet fluidly coupled to the compressor train or a source of high-pressure steam. Each respective vapor outlet of the steam recirculation manifold is fluidly coupled to a vapor inlet of a corresponding flash vessel in the flash vessel structure.

Description

Attorney Docket No, : 136048-5006-WQRecirculating Flash Vessel StructuresCROSS-REFERENCE TO RELATED APPLICATION

[0001] The present Application claims priority to United States Provisional Patent Application No.: 63 / 735,603, entitled “Grid Responsive Multi-Stage Mechanical Vapor Recompression System Controls,” filed December 18, 2024, United States Provisional Patent Application No.: 63 / 735,615, entitled “Hybrid Energy Storage and Mechanical Vapor Recompression System,” filed December 18, 2024, United States Provisional Patent Application No.: 63 / 735,623, entitled “Modular Multi-Stage Mechanical Vapor Recompression System Design,” filed December 18, 2024, United States Provisional Patent Application No.: 63 / 735,625, entitled “Modular Multi-Stage Mechanical Vapor Recompression System Design,” filed December 18, 2024, each of which is hereby incorporated by reference in its entirety for all purposes.TECHNICAL FIELD

[0002] The present disclosure relates generally to systems, methods, and apparatuses for producing high pressure steam, such as by a recirculating steam manifold (e.g., with waste heat generated at a facility).BACKGROUND

[0003] Reducing on-site emissions in the industrial sector is critical to achieving desired greenhouse gas targets. For example, one set of greenhouse gas targets are set forth in California’s Air Resources Board’s AB32 and SB 32 greenhouse gas reduction targets, although this particular set of greenhouse gas targets should not be deemed the only targets to meet in the industrial sector. Presently, industrial manufacturing processes generate thermal energy that needs to be dissipated from these processes. For example, waste heat may be transferred to a cooling water loop, which increases the temperature of the cooling water. The hot cooling water may then be sent to a cooling tower where the thermal energy is dissipated to atmosphere to reduce the temperature of the cooling water.

[0004] To comply with greenhouse gas targets and become carbon neutral, it is desired to increase industrial electrification.

[0005] A barrier to achieving desired energy goals is a lack of efficient and economically attractive technologies to electrify the massive thermal energy demands associated with steam production in industry. State-of-the-art industrial heat pumps areAttorney Docket No. : 136048-5006-WO unable to reach the temperatures required to produce medium-high pressure saturated steam required by many industrial facilities. State-of-the-art electric boiler technologies, on the other hand, are indeed able to reach required temperatures and pressures, but they do so with a low coefficient of performance (COP) of 1.0 or less. This results in excessive electricity consumption, making these systems uneconomical to operate. Additionally, the high electricity consumption may add undue strain on the electric power grid.

[0006] It would also be desirable that development of an alternative technology to meet the demand for medium to high pressure saturated steam could be implemented in a manner that limits custom engineering and specialized, one-off field assemblies. Custom engineering and specialized field assemblies drastically limit availability and increase cost. Further, customized solutions with specialized field assemblies could potentially require very costly downtime, and thus industrial customers are reluctant to try new technologies that may be perceived as possibly failing and / or causing undesired downtime.

[0007] Furthermore, one of skill in the art will appreciate that conventional flash vessel structures typically face several challenges, particularly in terms of efficiency, scalability, and adaptability to varying operational conditions. Conventional structures often lack modularity, making them difficult to customize for different facilities with varying steam flow rates, pressure requirements, and waste heat sources. Additionally, traditional designs frequently suffer from inefficiencies due to improper system layouts, excessive pressure drops, and limited turn-down capabilities, which restrict an ability to operate effectively under low-demand or high-demand conditions.

[0008] Another significant limitation of existing systems is their inability to effectively manage condensate and recirculated steam in a compact and modular manner. Conventional systems often require individual lines for each fan stage or rely on a single common drain line, both of which introduce operational inefficiencies. For instance, high- pressure fans draining into low-pressure lines causes excessive flashing of liquid to vapor, leading to high velocities, noise, erosion, and pressure drops that compromise system performance. Similarly, conventional steam recirculation systems lack the flexibility to support advanced operating modes, such as closed-loop operation or anti-surge control, which are necessary for maintaining system stability and efficiency.

[0009] Moreover, in multistage flash systems, each compressor receives a substantially different flow rate of steam. After each progressive stage, the flow rate increases as more flash steam is combined with the discharge of steam from the previous stage.Therefore, using a single recirculation or recycle valve at the front of the train is problematicAttorney Docket No. : 136048-5006-WO as recycling only the steam that the first stage uses causes subsequent stages to have insufficient flow, risking surge. Additionally, recycling too much steam to the first stage in an effort to avoid surging in later stages causes the first stage to perform inadequately and not achieve sufficient compression.

[0010] Therefore, a need exists for an improved system and method that addresses one or more of the above-described disadvantages, in a manner that is cost-effective, efficient, reliable, scalable, etc.SUMMARY

[0011] Given the above background, what is needed in the art are systems and methods to produce high pressure steam, such as by utilizing waste heat generated at a facility, thereby enhancing an overall energy consumption efficiency level and reducing associated manufacturing, installation, and operating costs. Accordingly, various aspects of the present disclosure are directed to systems, methods, and apparatuses for producing high- pressure steam. For instance, in some embodiments, the systems, methods, and apparatuses of the present disclosure are configured to utilize waste heat.

[0012] Systems, methods, and apparatuses for producing high-pressure steam are provided. In some embodiments, the systems, methods, and apparatuses address the technical problem of efficiently generating high-pressure steam in a modular and flexible manner, particularly for facilities with varying operational demands. In some embodiments, a compressor train includes a series of at least two compressors, an inlet, and an outlet providing high-pressure steam. In some embodiments, the use of multiple compressors in series enables staged compression, which is necessary for achieving the desired pressure while allowing for the integration of a steam recirculation manifold to prevent surge and enable flexible operation modes. In some embodiments, a flash vessel structure includes a series of at least two flash vessels, a terminal flash vessel at one end of the flash vessel structure, and a vapor outlet of the terminal flash vessel fluidly coupled to the inlet of the compressor train. This configuration of the flash vessel structure allows for efficient separation and management of vapor and liquid phases. Furthermore, in some embodiments, by coupling the terminal flash vessel to the compressor train, the system recirculates steam via a steam recirculation manifold as needed for startup, shutdown, or anti-surge operation. In some embodiments, vapor outlets of a remainder of the series of at least two flash vessels are fluidly coupled between compressors of the series of at least two compressors. In some embodiments, this staged coupling ensures that steam at various pressures is efficientlyAttorney Docket No. : 136048-5006-WO routed to the appropriate compressor stage, supporting both standard operation and recirculation scenarios to maintain system stability and efficiency. In some embodiments, the steam recirculation manifold includes a vapor inlet fluidly coupled to the outlet of the compressor train or a source of high-pressure steam, such as a boiler, a heat recovery steam generator, or other steam generation device, and one or more vapor outlets. In some embodiments, the recirculation manifold enables closed-loop operation of the system, antisurge control, and rapid system response to changing demand by allowing high-pressure steam to be selectively redirected. In some embodiments, each respective vapor outlet in the one or more vapor outlets is fluidly coupled upstream the compressor train. In some embodiments, each respective vapor outlet of the one or more vapor outlets is fluidly coupled upstream of a corresponding compressor of the compressor train. In some embodiments, each respective vapor outlet in the one or more vapor outlets is fluidly coupled to a vapor inlet of a corresponding flash vessel in the flash vessel structure. In some embodiments, this fluid coupling of the vapor outlets allows for precise control of steam flow back into the system, supporting modularity and operational flexibility. Moreover, in some embodiments, the steam recirculation manifold allows the system to address surge prevention, efficient turndown, and / or reliable startup and shutdown in high-pressure steam production systems. Furthermore, in some embodiments, the steam recirculation manifold allows each source of flash steam needs its own recycle valve to better tune flow through the train to avoid surge and excess steam. However, the present disclosure is not limited thereto.

[0013] Turning to more specific aspects, one aspect of the present disclosure is directed to providing a system for producing high pressure steam. The includes a compressor train, a flash vessel structure, and a steam recirculation manifold. The compressor train includes a series of at least two compressors, and inlet, and an outlet. The outlet of the compressor train is configured to provide high-pressure steam to a facility. The flash vessel structure includes a series of at least two flash vessels that include a terminal flash vessel at one end of the flash vessel structure. Moreover, a vapor outlet of the terminal flash vessel is fluidly coupled to the inlet of the compressor train. Vapor outlets of a remainder of the series of at least two flash vessels are fluidly coupled between compressors of the series of at least two compressors. Additionally, the steam recirculation manifold includes a vapor inlet that is fluidly coupled to the outlet of the compressor train or a source of high-pressure steam, such as a boiler, and one or more vapor outlets. In some embodiments, each respective vapor outlet in the one or more vapor outlets is fluidly coupled to a vapor inlet of a corresponding flash vessel in the flash vessel structure. In some embodiments, each respective vapor outlet of theAttorney Docket No. : 136048-5006-WO one or more vapor outlets is fluidly coupled upstream the compressor train. In some embodiments, each respective vapor outlet of the one or more vapor outlets is fluidly coupled upstream of a corresponding compressor of the compressor train.

[0014] In some embodiments, the one or more vapor outlets of the steam recirculation manifold includes a one-to-one relationship with the vapor outlets of the compressor train.

[0015] In some embodiments, the one or more vapor outlets of the steam recirculation manifold includes a one-to-many relationship with the vapor outlets of the compressor train.

[0016] In some embodiments, the one or more vapor outlets includes a single vapor outlet.

[0017] In some embodiments, the one or more vapor outlets includes at most 20 vapor outlets.

[0018] In some embodiments, the source of high-pressure steam is a boiler, a heat recovery steam generator, or other steam generation device.

[0019] In some embodiments, a branch angle between a distributor channel of the steam recirculation manifold and an intermediate channel of the steam recirculation manifold is 90° or about / approximately 90°.

[0020] In some embodiments, the branch angle between a distributor channel of the steam recirculation manifold and an intermediate channel of the steam recirculation manifold is obtuse (greater than 90°).

[0021] In some embodiments, the steam recirculation manifold is configured to induce flow via a pressure gradient between the vapor inlet and the one or more vapor outlets of the steam recirculation manifold.

[0022] In some embodiments, the steam recirculation manifold is configured to induce flow via a pressure gradient between the vapor inlet of the steam recirculation manifold and an inlet of the terminal flash vessel of the flash vessel structure.

[0023] In some embodiments, a first valve selectively controls fluid communication between the outlet of the compressor train and (i) the facility (ii) and the steam recirculation manifold.

[0024] In some embodiments, the first valve is configured to operate in a first position allowing a selected portion (up to the fill flow capacity, e.g., at most 100 volume percent (vol%)) of the high-pressure steam to flow from the outlet of the compressor train to the facility.

[0025] In some embodiments, the first valve is configured to operate in a second position allowing a selected portion (up to the full flow capacity, e.g., at most 100 vol%) ofAttorney Docket No. : 136048-5006-WO the high-pressure steam to flow from the outlet of the compressor train to the steam recirculation manifold.

[0026] In some embodiments, the first valve is configured to operate in a third position allowing a controlled fraction of the high-pressure steam (less than the full flow capacity, e.g., less than 100 vol%) of the high-pressure steam to flow to either the facility or the steam recirculation manifold.

[0027] In some embodiments, the system further includes a controller electronically coupled to the first valve and configured to adjust or modulate a position of the first valve between at least two positions.

[0028] In some embodiments, a second valve selectively controls fluid communication between the distributor channel of the steam recirculation manifold and the intermediate channel of the steam recirculation manifold to regulate the flow of recirculated steam.

[0029] In some embodiments, the second valve is configured to operate in a first position allowing a selected portion (up to the full flow capacity, e.g., at most 100 volume percent (vol%)) of the high-pressure steam to flow from the distributor channel to the intermediate channel.

[0030] In some embodiments, the second valve is configured to operate in a second position allowing a selected portion (up to the full flow capacity, e.g., at most 100 vol%) of the high-pressure steam to flow from the distributor channel to the intermediate channel.

[0031] In some embodiments, the second valve is configured to operate in a third position allowing a controlled fraction (less than the full flow capacity, e.g., less than 100 vol%) of the high-pressure steam to flow from the distributor channel to the intermediate channel.

[0032] In some embodiments, the system further includes a controller electronically coupled to the second valve and configured to adjust or modulate a position of the second valve between at least two positions.

[0033] In some embodiments, the system further includes a first sensor configured to detect a pressure associated with the compressor train, and the controller is electrically coupled to the first sensor and to the first valve and / or the second valve and is configured to maintain the pressure of the compressor train.

[0034] In some embodiments, the system further includes a second sensor configured to detect a pressure associated with the flash vessel structure, and the controller is electricallyAttorney Docket No. : 136048-5006-WO coupled to the second sensor and to the second valve and is configured to maintain the pressure of the flash vessel structure.

[0035] In some embodiments, the system further includes a third sensor configured to detect a pressure associated with the steam recirculation manifold, and the controller is electrically coupled to the third sensor and to both (i) the first valve and (ii) the second valve and is configured to maintain the pressure of the steam recirculation manifold.

[0036] In some embodiments, the system further includes a fourth sensor configured to detect a flow rate associated with the compressor train, and the controller that is electrically coupled to the fourth sensor and the first valve and / or the second valve is further configured to maintain the flow rate of the compressor train.

[0037] In some embodiments, the system further includes a fifth sensor configured to detect a flow rate associated with the flash vessel structure, and the controller is electrically coupled to the fifth sensor and to the second valve and is configured to maintain the flow rate of the flash vessel structure.

[0038] In some embodiments, the system further includes a sixth sensor configured to detect a flow rate associated with the steam recirculation manifold, and the controller is electrically coupled to the sixth sensor and both (i) the first valve and (ii) the second valve and is configured to maintain the flow rate of the steam recirculation manifold.

[0039] In some embodiments, the system further includes a seventh sensor configured to detect a resource consumption parameter associated with the compressor train, and the controller is electrically coupled to the seventh sensor and the first valve and / or the second valve and is configured to maintain the resource consumption of the compressor train.

[0040] In some embodiments, the system further includes an eighth sensor configured to detect a resource consumption parameter associated with the flash vessel structure, and the controller is electrically coupled to the eighth sensor and the second valve and is configured to maintain the resource consumption of the flash vessel structure.

[0041] In some embodiments, the system further includes a ninth sensor configured to detect a resource consumption rate associated with the steam recirculation manifold, and the controller that is electrically coupled to the ninth sensor and both (i) the first valve and (ii) the second valve and is further configured to maintain the resource consumption of the steam recirculation manifold.

[0042] In some embodiments, a pitch of the distributor channel is 0° or substantially 0°.Attorney Docket No. : 136048-5006-WO

[0043] In some embodiments, the pitch of the intermediate channel is 0° or substantially 0°.

[0044] In some embodiments, the system further includes a drain manifold configured to receive liquid condensate from the steam recirculation manifold.

[0045] In some embodiments, the drain manifold includes at least one channel fluidly coupled between a reservoir of the drain manifold and the distributor channel and / or the intermediate channel.

[0046] In some embodiments, the at least one channel of drain manifold includes a one-to-many relationship with the intermediate channel of the compressor train.

[0047] In some embodiments, the at least one channel of drain manifold includes a single channel.

[0048] In some embodiments, the at least one channel of drain manifold includes at most 20 channels.

[0049] The systems, methods, and apparatuses of the present disclosure have other features and advantages which will be apparent from or are set forth in more detail in the accompanying drawings, which are incorporated herein, and the following Detailed Description, which together serve to explain certain principles of the present invention.BRIEF DESCRIPTION OF THE DRAWINGS

[0050] Figure l is a block diagram of an example high-pressure steam production heat pump system and corresponds to the system architecture referenced in Figures 2-9, in which dashed boxes represent optional elements, in accordance with some embodiments.

[0051] Figure 2 is a block diagram of an example high-pressure steam production heat pump system, in accordance with some embodiments.

[0052] Figure 3 is a block diagram of an example high-pressure steam production heat pump system having a steam recirculation manifold in a closed loop flow, in accordance with some embodiments.

[0053] Figure 4 is a block diagram of an example high-pressure steam production heat pump system having a steam recirculation manifold in an open loop flow, in accordance with some embodiments.

[0054] Figure 5 is a block diagram of an example high-pressure steam production heat pump system having a steam recirculation manifold, in accordance with some embodiments.Attorney Docket No. : 136048-5006-WO

[0055] Figure 6 is a block diagram of an example high-pressure steam production heat pump system having a steam recirculation manifold with no steam recirculation injection point between compressors, in accordance with some embodiments.

[0056] Figure 7 is a block diagram of an example high-pressure steam production heat pump system having a steam recirculation manifold with an alternate steam source supplying high-pressure steam, in accordance with some embodiments.

[0057] Figure 8 is a block diagram of an example high-pressure steam production heat pump system having a steam recirculation manifold with a stage bypass, in accordance with some embodiments.

[0058] Figure 9 is a block diagram of an example high-pressure steam production heat pump system having a steam recirculation manifold with a vapor outlet injection points immediately upstream of a corresponding compressor, in accordance with some embodiments.

[0059] Figure 10 is a block diagram illustrating an example computer system that is applied in a high-pressure steam production heat pump system, in accordance with some embodiments.

[0060] In the figures, reference numbers refer to the same or corresponding parts of the present invention throughout the several figures of the drawing.DESCRIPTION OF EMBODIMENTS

[0061] Systems, methods, and apparatuses for producing high-pressure steam are provided. A compressor train includes a series of at least two compressors, and inlet, and an outlet providing high-pressure steam. A flash vessel structure includes a series of at least two flash vessels, a terminal flash vessel at one end of the flash vessel structure, and a vapor outlet of the terminal flash vessel fluidly coupled to the inlet of the compressor train. Vapor outlets of a remainder of the series of at least two flash vessels are fluidly coupled between compressors of the series of at least two compressors. A steam recirculation manifold includes a vapor inlet fluidly coupled to the outlet of the compressor train or a source of high- pressure steam, such as a boiler, and one or more vapor outlets. In some embodiments, each respective vapor outlet in the one or more vapor outlets is fluidly coupled to a vapor inlet of a corresponding flash vessel in the flash vessel structure. In some embodiments, each respective vapor outlet of the one or more vapor outlets is fluidly coupled upstream the compressor train. In some embodiments, each respective vapor outlet of the one or moreAttorney Docket No. : 136048-5006-WO vapor outlets is fluidly coupled upstream of a corresponding compressor of the compressor train.

[0062] Reference will now be made in detail to embodiments, examples of which are illustrated in the accompanying drawings. In the following detailed description, numerous specific details are set forth in order to provide a thorough understanding of the present disclosure. However, it will be apparent to one of ordinary skill in the art that the present disclosure may be practiced without these specific details. In other instances, well-known methods, procedures, and components have not been described in detail so as not to unnecessarily obscure aspects of the embodiments.

[0063] It will also be understood that, although the terms first, second, etc. may be used herein to describe various elements, these elements should not be limited by these terms. These terms are only used to distinguish one element from another. For instance, a first compressor could be termed a second compressor, and, similarly, a second compressor could be termed a first compressor, without departing from the scope of the present disclosure. The first compressor and the second compressor are both compressors, but they are not the same compressor.

[0064] The terminology used in the present disclosure is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. As used in the description of the invention and the appended claims, the singular forms “a,” “an,” and “the” are intended to include the plural forms as well, unless the context clearly indicates otherwise. It will also be understood that the term “and / or” as used herein refers to and encompasses any and all possible combinations of one or more of the associated listed items. It will be further understood that the terms “comprises” and / or “comprising,” when used in this specification, specify the presence of stated features, integers, steps, operations, elements, and / or components, but do not preclude the presence or addition of one or more other features, integers, steps, operations, elements, components, and / or groups thereof.

[0065] The foregoing description includes example systems, methods, techniques, instruction sequences, and computing machine program products that embody illustrative implementations. For purposes of explanation, numerous specific details are set forth in order to provide an understanding of various implementations of the inventive subject matter. It will be evident, however, to those skilled in the art that implementations of the inventive subject matter may be practiced without these specific details. In general, well-known instruction instances, protocols, structures, and techniques have not been shown in detail.Attorney Docket No. : 136048-5006-WO

[0066] The foregoing description, for purpose of explanation, has been described with reference to specific implementations. However, the illustrative discussions below are not intended to be exhaustive or to limit the implementations to the precise forms disclosed. Many modifications and variations are possible in view of the above teachings. The implementations are chosen and described in order to best explain the principles and their practical applications, to thereby enable others skilled in the art to best utilize the implementations and various implementations with various modifications as are suited to the particular use contemplated.

[0067] In the interest of clarity, not all of the routine features of the implementations described herein are shown and described. It will be appreciated that, in the development of any such actual implementation, numerous implementation-specific decisions are made in order to achieve the designer’s specific goals, such as compliance with use case- and business-related constraints, and that these specific goals will vary from one implementation to another and from one designer to another. Moreover, it will be appreciated that such a design effort might be complex and time-consuming, but nevertheless be a routine undertaking of engineering for those of ordering skill in the art having the benefit of the present disclosure.

[0068] As used herein, the term “if’ may be construed to mean “when” or “upon” or “in response to determining” or “in response to detecting,” depending on the context. Similarly, the phrase “if it is determined” or “if [a stated condition or event] is detected” may be construed to mean “upon determining” or “in response to determining” or “upon detecting [the stated condition or event]” or “in response to detecting [the stated condition or event],” depending on the context.

[0069] As used herein, the term “about” or “approximately” can mean within an acceptable error range for the particular value as determined by one of ordinary skill in the art, which can depend in part on how the value is measured or determined, e.g., the limitations of the measurement system. For example, “about” can mean within 1 or more than 1 standard deviation, per the practice in the art. “About” can mean a range of ± 20%, ± 10%, ± 5%, or ± 1% of a given value. Where particular values are described in the application and claims, unless otherwise stated, the term “about” means within an acceptable error range for the particular value. The term “about” can have the meaning as commonly understood by one of ordinary skill in the art. The term “about” can refer to ± 10%. The term “about” can refer to ± 5%.

[0070] As used herein, the term “epoch” means a predefined period of time.Attorney Docket No. : 136048-5006-WO

[0071] Furthermore, the terms “compressor” and “blower” are used interchangeably herein unless expressly stated otherwise.

[0072] The terms “flash vessel” and “knockout drum” are used interchangeably herein unless expressly stated otherwise.

[0073] The terms “steam” and “water vapor” are used interchangeably herein unless expressly stated otherwise.

[0074] Moreover, the term “stream” as used herein means any material moving or en route, directly or indirectly, from one location to another. In some embodiments, a stream is still a stream even if it is temporarily stationary for any epoch. In some embodiments, it will be understood that if the present disclosure refers to a particular stream, this does not necessarily refer to a single pipe or other physical conveyance.

[0075] It is noted that in various embodiments of this application, “connect” broadly means “directly connect” or “indirectly connected” via one or more intermediate structures.

[0076] Furthermore, when a reference number is given an “ith” denotation, the reference number refers to a generic component, set, or embodiment. For instance, a compressor termed “compressor i” refers to the ithcompressor in a plurality of compressors (e.g., a compressor 214-i in a plurality of compressors 214).

[0077] Figure 1 represents a block diagram of an example high-pressure steam production heat pump system, in which dashed boxes represent optional elements, in accordance with some embodiments. Figures 2-9 are block diagrams of detailed example high-pressure steam production heat pump systems, in which dashed boxes represent optional elements, in accordance with some embodiments.

[0078] Referring to Figure 1, in some embodiments, the present disclosure is directed to providing a system (e.g., system 104 of any of Figure 1-13, etc.) for producing high- pressure steam (e.g., high-pressure steam 140-1 or 140-2 of Figure 1A, high-pressure steam 140 of any of Figures 2, etc.).

[0079] In some embodiments, the system 104 is coupled to one or more facilities (e.g., first facility 102-1 of Figure 1A, second facility 102 of Figure 1A, etc.). For instance, in some embodiments, the system 104 is associated with a first facility 102-1 and disposed proximate to the first facility 102-1, which allows the system 104 to utilize one or more resources from the first facility 102-1. Moreover, in some embodiments, the system 104 is associated with the first facility 102-1 and disposed proximate to the first facility 102-1 in order to allow for the system 104 to provide the high-pressure steam 140 produced at theAttorney Docket No. : 136048-5006-WO system 104 to the first facility 102-1, such as by coupling to an existing steam header of the first facility 102-1. However, the present disclosure is not limited thereto.

[0080] Figure 2 is a block diagram of an example high-pressure steam production heat pump system, in accordance with some embodiments. In some embodiments, the system includes a flash vessel structure and a series of at least two compressors (e.g., series of at least two compressors 214 of any of Figures 2-9, efc.) and a flash vessel structure (e.g., flash vessel structure 202 of any of Figures 2-9, efc.), which collectively are utilized by the system 104 to produce the high-pressure steam 140 for a facility 102.

[0081] Additional details and information regarding the production of high-pressure steam using flash vessels and compressors is found at International Patent Application Publication No. : WO 2024 / 039878 Al, entitled “Systems, Methods, and Apparatuses for Producing High-Pressure Stream,” filed August 18, 2023, International Patent Application Publication No. : WO 2024 / 039878 Al, entitled “Systems, Methods, and Apparatuses for Utilizing Heat,” filed August 12, 2024, and International Patent Application Publication No.: WO 2025 / 184595 Al, entitled “Cascading Flash vessel Structures,” filed February 28, 2025, each of which is hereby incorporated by reference in its entirety for all purposes.

[0082] In some embodiments, the flash vessel structure 202 includes a series of at least two flash chambers (e.g., series 204 of Figure 2, series 204 of Figure 3, first series 204-1 of Figure 4, second series 204-2 of Figure 4, series 204 of Figure 6, etc.}. In some embodiments, the series of at least two flash chambers 204 includes a first flash chamber (e.g., first flash chamber 206-1 of Figure 2) and a second flash chamber (e.g., second flash chamber 206-2 of Figure 2, etc. , which allows for utilizing cascading flash chambers.

[0083] In some embodiments, each flash chamber 206 in the series of at least two flash chambers 204 is configured to be maintained (e.g, by control module 906 of Figure 10) at a predetermined internal pressure or predetermined internal pressure range that is less than a saturation pressure of the liquid media received by the flash vessel structure 202. For instance, in some embodiments, each respective flash vessel 206 is configured to be maintained at an internal pressure that is less than a saturation pressure of the liquid media water received at the liquid inlet 606 into the respective flash chamber 206. However, the present disclosure is not limited thereto. Moreover, each flash chamber 206 in the series of at least two flash chambers 204 is configured to expand the liquid media that is received by the liquid inlet of the flash chamber 206 to produce low-pressure steam.

[0084] In some embodiments, the series of at least two flash chambers 204 includes between two and twenty flash chambers 206, between two and seventeen flash chambers 206,Attorney Docket No. : 136048-5006-WO between two and fifteen flash chambers 206, between two and twelve flash chambers 206, between two and nine flash chambers 206, between two and six flash chambers 206, between two and three flash chambers 206, between three and twenty flash chambers 206, between three and seventeen flash chambers 206, between three and fifteen flash chambers 206, between three and twelve flash chambers 206, between three and nine flash chambers 206, between three and six flash chambers 206, between five and twenty flash chambers 206, between five and seventeen flash chambers 206, between five and fifteen flash chambers 206, between five and twelve flash chambers 206, between five and nine flash chambers 206, between five and six flash chambers 206, between seven and twenty flash chambers 206, between seven and seventeen flash chambers 206, between seven and fifteen flash chambers 206, between seven and twelve flash chambers 206, between seven and nine flash chambers 206, between nine and twenty flash chambers 206, between nine and seventeen flash chambers 206, between nine and fifteen flash chambers 206, between nine and twelve flash chambers 206, between eleven and twenty flash chambers 206, between eleven and seventeen flash chambers 206, between eleven and fifteen flash chambers 206, between eleven and twelve flash chambers 206, between thirteen and twenty flash chambers 206, between thirteen and seventeen flash chambers 206, between thirteen and fifteen flash chambers 206, between fifteen and twenty flash chambers 206, between fifteen and seventeen flash chambers 206, or between seventeen and twenty flash chambers 206, inclusive. In some embodiments, the series of at least two flash chambers 204 includes at least two flash chambers 206, at least three flash chambers 206, at least four flash chambers 206, at least five flash chambers 206, at least six flash chambers 206, at least seven flash chambers 206, at least eight flash chambers 206, at least nine flash chambers 206, at least ten flash chambers 206, at least eleven flash chambers 206, at least twelve flash chambers 206, at least thirteen flash chambers 206, at least fourteen flash chambers 206, at least fifteen flash chambers 206, at least sixteen flash chambers 206, at least seventeen flash chambers 206, at least eighteen flash chambers 206, at least nineteen flash chambers 206, or at least twenty flash chambers 206. In some embodiments, the series of at least two flash chambers 204 includes at most two flash chambers 206, at most three flash chambers 206, at most four flash chambers 206, at most five flash chambers 206, at most six flash chambers 206, at most seven flash chambers 206, at most eight flash chambers 206, at most nine flash chambers 206, at most ten flash chambers 206, at most eleven flash chambers 206, at most twelve flash chambers 206, at most thirteen flash chambers 206, at most fourteen flash chambers 206, at most fifteen flash chambers 206, at most sixteen flash chambers 206, at most seventeen flash chambers 206, atAttorney Docket No. : 136048-5006-WO most eighteen flash chambers 206, at most nineteen flash chambers 206, or at most twenty flash chambers 206. However, the present disclosure is not limited thereto.

[0085] In some embodiments, the first flash chamber 206-1 is located at a first end of the flash vessel structure 202 and the second flash chamber located at a second end of the flash vessel structure 202. In some such embodiments, the second end is opposite the first end of the flash vessel structure 202, which creates spatial separation between the first flash chamber 206-2 and the second flash chamber 206-1. As a non-limiting example, in some embodiments, the first flash chamber 206-1 is an initial terminal flash chamber in the series of at least two flash chambers 204 and the second flash chamber 206-2 is a final terminal flash chamber in the series of at least two flash chambers 204. For instance, referring briefly to Figure 2, a first flash chamber 206-1 is a first terminal flash chamber 206 of the series of at least two flash chambers 204 at one end of the flash vessel structure 202 and a second flash chamber 206-2 is a second terminal flash chamber 206 of the series of at least two flash chambers 204 at a second end of the flash vessel structure 202. Moreover, in some embodiments, each flash chamber 206 of the at least two flash chambers 204 includes a cross section that is perpendicular to the horizontal (e.g., a horizontal direction of flow of the liquid media, the horizon, etc.}.

[0086] In some embodiments, the flash vessel structure 202 is configured to receive a liquid media (e.g., hot water 110 of Figures 1-9) flow via a liquid input (e.g, liquid input 208 of Figure 2) formed on the first flash chamber 206-1, flash evaporate a portion of the liquid media flow 110 to generate a vapor, and drain the liquid media flow 110 via a liquid outlet (e.g, liquid outlet 210 of Figure 2, etc. formed on the second flash chamber 206-2. By way of example, in some embodiments, each flash chamber 206 includes a liquid input for receiving a liquid media, a vapor orifice configured to stay above the liquid media and convey vaper flashed at the flash chamber 206 to a compressor 216, and a liquid outlet 608 configured to convey the liquid media to the liquid outlet 210 of the series of at least two flash chambers 204 or an adjacent flash chamber 206. However, the present disclosure is not limited thereto.

[0087] In some embodiments, a flow rate of the liquid media flow 110 through some or all of the flash vessel structure 202 is between 0.5 meters per second (m / s) and 2 m / s. In some embodiments, the flow rate of the liquid media flow through some or all of the flash structure is between 5 and 20 m / s, 5 and 12 m / s, 6 and 19 m / s, 6 and 11 m / s, 7 and 18 m / s, 7 and 10 m / s, 8 and 17 m / s, 8 and 9 m / s, 9 and 16 m / s, 10 and 15 m / s, 11 and 14 m / s, 12 and 13 m / s, 12 and 20 m / s, 13 and 19 m / s, 14 and 18 m / s, or 15 and 17 m / s. In some embodiments,Attorney Docket No. : 136048-5006-WO the flow rate of the liquid media flow through some or all of the flash structure is at least 5 m / s, at least 6 m / s, at least 7 m / s, at least 8 m / s, at least 9 m / s, at least 10 m / s, at least 11 m / s, at least 12 m / s, at least 13 m / s, at least 14 m / s, at least 15 m / s, at least 16 m / s, at least 17 m / s, at least 18 m / s, at least 19 m / s, or at least 20 m / s. In some embodiments, the flow rate of the liquid media flow through some or all of the flash structure is at most 5 m / s, at most 6 m / s, at most 7 m / s, at most 8 m / s, at most 9 m / s, at most 10 m / s, at most 11 m / s, at most 12 m / s, at most 13 m / s, at most 14 m / s, at most 15 m / s, at most 16 m / s, at most 17 m / s, at most 18 m / s, at most 19 m / s, or at most 20 m / s.

[0088] In some embodiments, the system 104 is configured to receive the liquid media 110 at a first temperature. In some embodiments, the first temperature is between 60 degrees Fahrenheit (°F) (15.6 degrees Celsius (°C)) and 150 °F (65.6 °C). In some embodiments, the first temperature is between 60 °F (15.6 °C) and 220 °F (104 °C). For instance, in some embodiments, the first temperature is between 60 °F (15.6 °C) and 220 °F (65.6 °C), between 60 °F (15.6 °C) and 205 °F (96.1 °C), between 60 °F (15.6 °C) and 190 °F(87.8 °C), between 60 °F (15.6 °C) and 175 °F (79.4 °C), between 60 °F (15.6 °C) and 150 °F(65.6 °C), between 60 °F (15.6 °C) and 135 °F (57.2 °C), between 60 °F (15.6 °C) and 120 °F(48.9 °C), between 60 °F (15.6 °C) and 105 °F (40.6 °C), between 60 °F (15.6 °C) and 90 °F(32.2 °C), between 60 °F (15.6 °C) and 75 °F (23.9 °F), between 80 °F (26.7 °C) and 220 °F (65.6 °C), between 80 °F (26.7 °C) and 205 °F (96.1 °C), between 80 °F (26.7 °C) and 190 °F(87.8 °C), between 80 °F (26.7 °C) and 175 °F (79.4 °C), between 80 °F (26.7 °C) and 150 °F(65.6 °C), between 80 °F (26.7 °C) and 135 °F (57.2 °C), between 80 °F (26.7 °C) and 120 °F(48.9 °C), between 80 °F (26.7 °C) and 105 °F (40.6 °C), between 80 °F (26.7 °C) and 90 °F(32.2 °C), between 100 °F (37.8 °C) and 220 °F (65.6 °C), between 100 °F (37.8 °C) and 205 °F (96.1 °C), between 100 °F (37.8 °C) and 190 °F (87.8 °C), between 100 °F (37.8 °C) and 175 °F (79.4 °C), between 100 °F (37.8 °C) and 150 °F (65.6 °C), between 100 °F (37.8 °C) and 135 °F (57.2 °C), between 100 °F (37.8 °C) and 120 °F (48.9 °C), between 100 °F (37.8 °C) and 105 °F (40.6 °C), between 120 °F (48.9 °C) and 220 °F (65.6 °C), between 120 °F (48.9 °C) and 205 °F (96.1 °C), between 120 °F (48.9 °C) and 190 °F (87.8 °C), between 120 °F (48.9 °C) and 175 °F (79.4 °C), between 120 °F (48.9 °C) and 150 °F (65.6 °C), between 120 °F (48.9 °C) and 135 °F (57.2 °C), between 140 °F (60.0 °C) and 220 °F (65.6 °C), between 140 °F (60.0 °C) and 205 °F (96.1 °C), between 140 °F (60.0 °C) and 190 °F (87.8 °C), between 140 °F (60.0 °C) and 175 °F (79.4 °C), between 140 °F (60.0 °C) and 150 °F (65.6 °C), between 175 °F (79.4 °C), and 220 °F (65.6 °C), between 175 °F (79.4 °C), and 205 °F (96.1 °C), between 175 °F (79.4 °C), and 190 °F (87.8 °C), between 190 °F (87.8 °C)Attorney Docket No. : 136048-5006-WO and 220 °F (65.6 °C), between 190 °F (87.8 °C) and 205 °F (96.1 °C), or between 205 °F (96.1 °C) and 220 °F (65.6 °C), inclusive. In some embodiments, the first temperature from is at least 60 °F (15.6 °C), at least 65 °F (18.3 °C), at least 70 °F (21.1 °C), at least 75 °F (23.9 °C), at least 80 °F (26.7 °C), at least 85 °F (29.4 °C), at least 90 °F (32.2 °C), at least 95 °F (35.0 °C), at least 100 °F (37.8 °C), 105 °F (40.6 °C), at least 110 °F (43.3 °C), at least 115 °F (46.1 °C), at least 120 °F (48.9 °C), at least 125 °F (51.7 °C), at least 130 °F (54.4 °C), at least 135 °F (57.2 °C), at least 140 °F (60.0 °C), at least 145 °F (62.8 °C), at least 150 °F (65.6 °C), at least 155 °F (68.3 °C), at least 160 °F (71.1 °C), at least 165 °F (73.9 °C), at least 170 °F (76.7 °C), at least 175 °F (79.4 °C), at least 180 °F (82.2 °C), at least 185 °F (85.0 °C), at least 190 °F (87.8 °C), at least 195 °F (90.6 °C), at least 200 °F (93.3 °C), at least 205 °F (96.1 °C), at least 210 °F (98.9 °C), at least 215 °F (102 °C), or at least 220 °F (104 °C). In some embodiments, the first temperature is at most 60 °F (15.6 °C), at most 65 °F (18.3 °C), at most 70 °F (21.1 °C), at most 75 °F (23.9 °C), at most 80 °F (26.7 °C), at most 85 °F (29.4 °C), at most 90 °F (32.2 °C), at most 95 °F (35.0 °C), at most 100 °F (37.8 °C), 105 °F (40.6 °C), at most 110 °F (43.3 °C), at most 115 °F (46.1 °C), at most 120 °F (48.9 °C), at most 125 °F (51.7 °C), at most 130 °F (54.4 °C), at most 135 °F (57.2 °C), at most 140 °F (60.0 °C), at most 145 °F (62.8 °C), at most 150 °F (65.6 °C), at most 155 °F (68.3 °C), at most 160 °F (71.1 °C), at most 165 °F (73.9 °C), at most 170 °F (76.7 °C), at most 175 °F (79.4 °C), at most 180 °F (82.2 °C), at most 185 °F (85.0 °C), at most 190 °F (87.8 °C), at most 195 °F (90.6 °C), at most 200 °F (93.3 °C), at most 205 °F (96.1 °C), at most 210 °F (98.9 °C), at most 215 °F (102 °C), or at most 220 °F (104 °C). However, the present disclosure is not limited thereto.

[0089] In some embodiments, in order to provide the high-pressure steam 140 that is utilizable by the facility 102, the compressor train 212 includes a series of at least two compressors 214 (e.g., first compressor 216-1 of any of Figures 2-9, second compressor 216- 2 of any of Figures 2-9, third compressor 216-3 of any of Figures 2-9, etc. . By way of example, in some embodiments, the series of at least two compressors 214 draw vapor (e.g., via a pressure gradient generated at the compressor 216) at its vapor inlets and increases pressure at its vapor outlets. In some such embodiments, the flash chambers 206 provide vapor to the vapor inlets of the series of at least two compressors, and, therefore, operate at approximately the inlet pressure of corresponding compressor in the series of at least two compressors 214 the flash chamber is fluidly coupled to via the vapor out of the flash chamber.Attorney Docket No. : 136048-5006-WO

[0090] In some embodiments, the series of at least two compressors 214 includes the first compressor 216-1 and the second compressor 216-2. The first compressor 216-1 includes a first optimal inlet volumetric flow rate associated with a vapor inlet. Moreover, in some such embodiment, the second compressor 216-2 includes a second optimal inlet volumetric flow rate that is greater than the first optimal inlet volumetric flow rate of the first compressor 216-1. Furthermore, in some such embodiment, the second optimal inlet volumetric flow rate that is equal or substantially equal to the first optimal inlet volumetric flow rate of the first compressor 216-1. Additionally, in some such embodiment, the second optimal inlet volumetric flow rate that is less than to the first optimal inlet volumetric flow rate of the first compressor 216-1. Moreover, in some such embodiments, the first compressor 216-1 is coupled upstream of the second compressor 216-2 in the series of at least two compressors 214.

[0091] Furthermore, in some embodiments, each compressor 216 in the series of at least two compressors 214 is a single-stage compressor 216. For instance, in some embodiments, each stage of each compressor 216 is associated with a corresponding motor (e.g., power supply 986 of Figure 10) and / or a corresponding variable frequency drive (VFD) controller (e.g., controller 906 of Figure 10), which allows for a respective compressor 216 to be individually operated distinctly from the remainder of the series of at least two compressors 214.

[0092] For instance, in some embodiments, the series of at least two compressors 214 includes between two and twenty compressors 216 (e.g., two compressors 216, three compressors 216, . . twenty compressors 216, efc.), between two and seventeen compressors 216, between two and fifteen compressors 216, between two and twelve compressors 216, between two and nine compressors 216, between two and six compressors 216, between two and three compressors 216, between three and twenty compressors 216, between three and seventeen compressors 216, between three and fifteen compressors 216, between three and twelve compressors 216, between three and nine compressors 216, between three and six compressors 216, between five and twenty compressors 216, between five and seventeen compressors 216, between five and fifteen compressors 216, between five and twelve compressors 216, between five and nine compressors 216, between five and six compressors 216, between seven and twenty compressors 216, between seven and seventeen compressors 216, between seven and fifteen compressors 216, between seven and twelve compressors 216, between seven and nine compressors 216, between nine and twenty compressors 216, between nine and seventeen compressors 216, between nine and fifteenAttorney Docket No. : 136048-5006-WO compressors 216, between nine and twelve compressors 216, between eleven and twenty compressors 216, between eleven and seventeen compressors 216, between eleven and fifteen compressors 216, between eleven and twelve compressors 216, between thirteen and twenty compressors 216, between thirteen and seventeen compressors 216, between thirteen and fifteen compressors 216, between fifteen and twenty compressors 216, between fifteen and seventeen compressors 216, or between seventeen and twenty compressors 216, inclusive. In some embodiments, the series of at least two compressors 214 includes at least two compressors 216, at least three compressors 216, at least four compressors 216, at least five compressors 216, at least six compressors 216, at least seven compressors 216, at least eight compressors 216, at least nine compressors 216, at least ten compressors 216, at least eleven compressors 216, at least twelve compressors 216, at least thirteen compressors 216, at least fourteen compressors 216, at least fifteen compressors 216, at least sixteen compressors 216, at least seventeen compressors 216, at least eighteen compressors 216, at least nineteen compressors 216, or at least twenty compressors 216. In some embodiments, the series of at least two compressors 214 includes at most two compressors 216, at most three compressors 216, at most four compressors 216, at most five compressors 216, at most six compressors 216, at most seven compressors 216, at most eight compressors 216, at most nine compressors 216, at most ten compressors 216, at most eleven compressors 216, at most twelve compressors 216, at most thirteen compressors 216, at most fourteen compressors 216, at most fifteen compressors 216, at most sixteen compressors 216, at most seventeen compressors 216, at most eighteen compressors 216, at most nineteen compressors 216, or at most twenty compressors 216.

[0093] In some embodiments, each compressor 216 in the series of at least two compressors 214 and each flash vessel 206 in the series of at least two flash chambers 204 share a one-to-one relationship. For instance, referring briefly to Figure 2, the system 104 depicts the one-to-one relationship for each compressor 216 and each flash chamber 206, in that the series of at least two compressors 214 has two compressors 216 and the series of at least two flash chambers 204 similarly has two flash chambers 206. In some embodiments, the compressors 216 and flash chambers 206 share the one-to-one relationship when a temperature difference between a first compressor and a second compressor satisfies a threshold temperature, such as 10 °C, 20 °C, etc. In some embodiments, the compressors 216 and flash chambers 206 share the one-to-one relationship when a temperature difference between a first flash vessel and a second flash vessel satisfies a threshold temperature, suchAttorney Docket No. : 136048-5006-WO as 20 °C. Moreover, in some embodiments, each compressor 216 and each flash chamber 206 share a many-to-one relationship.

[0094] In some embodiments, the series of at least two compressors 214 includes m compressors 216, in which m is an integer, such as an integer greater than two. In some embodiments, m is at least two and less than twenty-one. Moreover, in some embodiments, m is selected for the system 104 in accordance with one or more input parameters (e.g., parameters 916 of Figure 10) of the system 104 and / or one or more output parameters 916 of the system 104. For instance, in some embodiments, m is selected in accordance with a temperature of the high-pressure steam 140 that is produced by the system 104 and a temperature of hot water received from the facility 102 or the different facility 102 by the system 104. In some embodiments, m is selected in accordance with a lift (e.g., difference) between the temperature of the high-pressure steam 140 that is produced by the system 104 and the temperature of the liquid media. For instance, in some embodiments, m is selected in order to provide the lift between 60 °F (15.6 °C) and 330 °F (165 °C), between 60 °F (15.6 °C) and 300 °F (149 °C), between 60 °F (15.6 °C) and 270 °F (135 °C), between 60 °F (15.6 °C) and 250 °F (121 °C), between 60 °F (15.6 °C) and 220 °F (65.6 °C), between 60 °F (15.6 °C) and 205 °F (96.1 °C), between 60 °F (15.6 °C) and 190 °F (87.8 °C), between 60 °F (15.6°C) and 175 °F (79.4 °C), between 60 °F (15.6 °C) and 150 °F (65.6 °C), between 60 °F (15.6°C) and 135 °F (57.2 °C), between 60 °F (15.6 °C) and 120 °F (48.9 °C), between 60 °F (15.6°C) and 105 °F (40.6 °C), between 60 °F (15.6 °C) and 90 °F (32.2 °C), between 60 °F (15.6°C) and 75 °F (23.9 °F), between 80 °F (26.7 °C) and 330 °F (165 °C), between 80 °F (26.7 °C) and 300 °F (149 °C), between 80 °F (26.7 °C) and 270 °F (135 °C), between 80 °F (26.7 °C) and 250 °F (121 °C), between 80 °F (26.7 °C) and 220 °F (65.6 °C), between 80 °F (26.7 °C) and 205 °F (96.1 °C), between 80 °F (26.7 °C) and 190 °F (87.8 °C), between 80 °F (26.7°C) and 175 °F (79.4 °C), between 80 °F (26.7 °C) and 150 °F (65.6 °C), between 80 °F (26.7°C) and 135 °F (57.2 °C), between 80 °F (26.7 °C) and 120 °F (48.9 °C), between 80 °F (26.7°C) and 105 °F (40.6 °C), between 80 °F (26.7 °C) and 90 °F (32.2 °C), between 100 °F (37.8°C) and 330 °F (165 °C), between 100 °F (37.8 °C) and 300 °F (149 °C), between 100 °F (37.8 °C) and 270 °F (135 °C), between 100 °F (37.8 °C) and 250 °F (121 °C), between 100 °F (37.8 °C) and 220 °F (65.6 °C), between 100 °F (37.8 °C) and 205 °F (96.1 °C), between 100 °F (37.8 °C) and 190 °F (87.8 °C), between 100 °F (37.8 °C) and 175 °F (79.4 °C), between 100 °F (37.8 °C) and 150 °F (65.6 °C), between 100 °F (37.8 °C) and 135 °F (57.2 °C), between 100 °F (37.8 °C) and 120 °F (48.9 °C), between 100 °F (37.8 °C) and 105 °F (40.6 °C), between 120 °F (48.9 °C) and 330 °F (165 °C), between 120 °F (48.9 °C) and 300Attorney Docket No. : 136048-5006-WO°F (149 °C), between 120 °F (48.9 °C) and 270 °F (135 °C), between 120 °F (48.9 °C) and 250 °F (121 °C), between 120 °F (48.9 °C) and 220 °F (65.6 °C), between 120 °F (48.9 °C) and 205 °F (96.1 °C), between 120 °F (48.9 °C) and 190 °F (87.8 °C), between 120 °F (48.9 °C) and 175 °F (79.4 °C), between 120 °F (48.9 °C) and 150 °F (65.6 °C), between 120 °F (48.9 °C) and 135 °F (57.2 °C), between 140 °F (60.0 °C) and 330 °F (165 °C), between 140 °F (60.0 °C) and 300 °F (149 °C), between 140 °F (60.0 °C) and 270 °F (135 °C), between 140 °F (60.0 °C) and 250 °F (121 °C), between 140 °F (60.0 °C) and 220 °F (65.6 °C), between 140 °F (60.0 °C) and 205 °F (96.1 °C), between 140 °F (60.0 °C) and 190 °F (87.8 °C), between 140 °F (60.0 °C) and 175 °F (79.4 °C), between 140 °F (60.0 °C) and 150 °F (65.6 °C), between 175 °F (79.4 °C)and 330 °F (165 °C), between 175 °F (79.4 °C)and 300 °F (149 °C), between 175 °F (79.4 °C)and 270 °F (135 °C), between 175 °F (79.4 °C)and 250 °F (121 °C), between 175 °F (79.4 °C), and 220 °F (65.6 °C), between 175 °F (79.4 °C), and 205 °F (96.1 °C), between 175 °F (79.4 °C), and 190 °F (87.8 °C), between 190 °F (87.8 °C) and 220 °F (65.6 °C), between 190 °F (87.8 °C) and 330 °F (165 °C), between 190 °F (87.8 °C) and 300 °F (149 °C), between 190 °F (87.8 °C) and 270 °F (135 °C), between 190 °F (87.8 °C) and 250 °F (121 °C), between 190 °F (87.8 °C) and 205 °F (96.1 °C), between 205 °F (96.1 °C) and 330 °F (165 °C), between 205 °F (96.1 °C) and 300 °F (149 °C), between 205 °F (96.1 °C) and 270 °F (135 °C), between 205 °F (96.1 °C) and 250 °F (121 °C), between 205 °F (96.1 °C) and 220 °F (65.6 °C), between 250 °F (121 °C)and 330 °F (165 °C), between 250 °F (121 °C) and 300 °F (149 °C), between 250 °F (121 °C) and 270 °F (135 °C), between 270 °F (135 °C), and 330 °F (165 °C), between 330 °F (165 °C) and 392 °F (200 °C) inclusive. In some embodiments, m is selected in order to provide the lift of at least 60 °F (15.6 °C), at least 65 °F (18.3 °C), at least 70 °F (21.1 °C), at least 75 °F (23.9 °C), at least 80 °F (26.7 °C), at least 85 °F (29.4 °C), at least 90 °F (32.2 °C), at least 95 °F (35.0 °C), at least 100 °F (37.8 °C), 105 °F (40.6 °C), at least 110 °F (43.3 °C), at least 115 °F (46.1 °C), at least 120 °F (48.9 °C), at least 125 °F (51.7 °C), at least 130 °F (54.4 °C), at least 135 °F (57.2 °C), at least 140 °F (60.0 °C), at least 145 °F (62.8 °C), at least 150 °F (65.6 °C), at least 155 °F (68.3 °C), at least 160 °F (71.1 °C), at least 165 °F (73.9 °C), at least 170 °F (76.7 °C), at least 175 °F (79.4 °C), at least 180 °F (82.2 °C), at least 185 °F (85.0 °C), at least 190 °F (87.8 °C), at least 195 °F (90.6 °C), at least 200 °F (93.3 °C), at least 205 °F (96.1 °C), at least 210 °F (98.9 °C), at least 215 °F (102 °C), at least 220 °F (104 °C), at least 250 °F (121 °C), at least 270 °F (135 °C), at least 300 °F (149 °C), at least 330 °F (165 °C), or at least 392 °F (200 °C). In some embodiments, m is selected in order to provide the lift of at most 60 °F (15.6 °C), at most 65 °F (18.3 °C), at most 70 °F (21.1 °C), atAttorney Docket No. : 136048-5006-WO most 75 °F (23.9 °C), at most 80 °F (26.7 °C), at most 85 °F (29.4 °C), at most 90 °F (32.2 °C), at most 95 °F (35.0 °C), at most 100 °F (37.8 °C), 105 °F (40.6 °C), at most 110 °F (43.3 °C), at most 115 °F (46.1 °C), at most 120 °F (48.9 °C), at most 125 °F (51.7 °C), at most 130 °F (54.4 °C), at most 135 °F (57.2 °C), at most 140 °F (60.0 °C), at most 145 °F (62.8 °C), at most 150 °F (65.6 °C), at most 155 °F (68.3 °C), at most 160 °F (71.1 °C), at most 165 °F (73.9 °C), at most 170 °F (76.7 °C), at most 175 °F (79.4 °C), at most 180 °F (82.2 °C), at most 185 °F (85.0 °C), at most 190 °F (87.8 °C), at most 195 °F (90.6 °C), at most 200 °F (93.3 °C), at most 205 °F (96.1 °C), at most 210 °F (98.9 °C), at most 215 °F (102 °C), at most 220 °F (104 °C), at most 250 °F (121 °C), at most 270 °F (135 °C), at most 300 °F (149 °C), at most 330 °F (165 °C), or at least 392 °F (200 °C).

[0095] In some embodiments, the series of at least two compressors 214 is configured such that the at least two compressors 216 in the series of at least two compressors 214 are fluidically coupled in series. In some embodiments, the series of at least two compressors 214 are coupled, at least in part, fluidically in series, which allows for a stream of vapor medium to flow from a first compressor 216-1 in the series of at least two compressors 216 into a second compressor 216-2 in the series of at least two compressors 216, or from a first flash chamber to the first compressor 216-1 and further to the second compressor 216-2. However, the present disclosure is not limited thereto.

[0096] Furthermore, in some embodiments, the series of at least two compressors 214 is coupled to the flash vessel structure 202, in which every two immediately adjacent compressors 214 are coupled via a vapor channel (e.g., first vapor channel 214-1 of Figure 2, second vapor channel 214-2 of Figure 2, etc.), which allows for each compressor 216 of the compressor train 212 to receive vapor flashed by the respective flash chamber 206. In this way, in some embodiments, each compressor 216 is configured to compress at least the vapor received from the respective flash chamber 206.

[0097] In some embodiments, the system 104 includes a steam recirculation manifold 260. In some embodiments, the steam recirculation manifold 260 allows the system to utilize some or all of the high-pressures steam produced by the compressor train 212, as opposed to providing all of the high pressure steam to a facility. For instance, in some embodiments, the steam recirculation manifold 260 includes a vapor inlet 262 that is fluidly coupled to the outlet of the compressor train 212 or a source of high-pressure steam, such as a boiler, which allows the steam recirculation manifold 260 to receive steam from the compressor train 212. Moreover, in some embodiments, the steam recirculation manifold 260 includes one or more vapor outlets 264, which allows for the steam recirculation manifold 260 to provide some orAttorney Docket No. : 136048-5006-WO all of the high-pressure steam received from the compressor train 212 back into a portion of the system 104, such as the flash vessel structure 202. For instance, in some embodiments, each respective vapor outlet 264 in the one or more vapor outlets 264 is fluidly coupled to a vapor inlet of a corresponding flash vessel in the flash vessel structure 202. However, the present disclosure is not limited thereto. In some embodiments, each respective vapor outlet of the one or more vapor outlets is fluidly coupled upstream of the compressor train. In some embodiments, each respective vapor outlet of the one or more vapor outlets is fluidly coupled upstream of a corresponding compressor of the compressor train. In some embodiments, each respective vapor outlet of the one or more vapor outlets is fluidly coupled upstream of a corresponding compressor of the compressor train. In some embodiments, upstream coupling positions the injection point at or proximate to the suction side of the corresponding compressor stage to increase local volume flow, maintain a defined surge margin, and / or stabilize the operating point at deep turndown. In some embodiments, one or more upstream connections are made through dedicated branch ducts, tees, or manifolds that route recirculated or auxiliary vapor to individual stage inlets without inducing excessive pressure loss or flow maldistribution. In some embodiments, the upstream coupling geometry maintains minimum straight-run length and angle constraints to preserve inlet flow quality, reduce swirl, and limit dynamic losses, thereby improving compression efficiency and stage- to-stage controllability. In some embodiments, the upstream coupling is implemented for one, a subset, or all stages to tailor recirculation distribution according to stage lift, inlet density, and surge propensity.

[0098] In some embodiments, the source of high-pressure steam is a boiler, heat recovery steam generator, or other steam generation device. In some embodiments, the boiler includes a gas-, oil-, biomass-, or electrically fired unit sized to maintain facility header pressure and provide trim or backup steam when the compressor train is turned down or isolated. In some embodiments, the heat recovery steam generator receives hot exhaust from a turbine, engine, or process heater and produces high-pressure steam that can be directed to the steam recirculation manifold, the system header, and / or the facility header.

[0099] In some embodiments, the vapor inlet 262 of the steam recirculation manifold 260 is directly connected to the outlet of the compressor train 212. For instance, in some embodiments, the vapor inlet 262 includes a horizontally oriented header, positioned above and / or adjacent to a side portion of the compressor train. In some embodiments, the vapor inlet 262 allows for a constant or variable diameter to accommodate different flow rates of high-pressure steam received by the steam recirculation manifold. In this way, in someAttorney Docket No. : 136048-5006-WO embodiments, the vapor include 262 of the steam recirculation manifold 260 allows for the recirculated steam to be efficiently routed back into the flash vessel structure 202, supporting various operational modes such as startup, anti-surge control, or closed-loop operation.

[0100] In some embodiments, the one or more vapor outlets of the steam recirculation manifold includes a one-to-one relationship with the vapor outlets of the compressor train. For instance, in some embodiments, each vapor outlet on the steam recirculation manifold is individually and directly fluidly coupled to a corresponding vapor inlet of the flash vessel structure. In some embodiments, each vapor outlet from the manifold aligns with a specific vapor inlet of a corresponding flash vessel, allowing for precise control and distribution of recirculated steam to each stage of the flash vessel structure. In some embodiments, this one- to-one arrangement is particularly advantageous for systems requiring tailored steam flow management at each flash vessel of the flash vessel structure, such as by enabling independent operation and monitoring of each recirculation path through the steam recirculation manifold 260.

[0101] In some embodiments, the one or more vapor outlets of the steam recirculation manifold includes a one-to-many relationship with the vapor outlets of the compressor train. In some embodiments, the one or more vapor outlets of the steam recirculation manifold is configured in the one-to-many relationship, in which a single vapor outlet from the manifold is fluidly coupled to one of multiple vapor inlet of the flash vessel structure. In some embodiments, one-to-many arrangement reduces the number of required manifold outlets and associated piping, which is beneficial for compact installations or when uniform steam distribution across multiple flash vessels is desired.

[0102] In some embodiments, the one or more vapor outlets includes a single vapor outlet. In some embodiments, the one or more vapor outlets includes at most 20 vapor outlets. In some embodiments, the one or more vapor outlets includes at least 1 vapor outlet, at least 2 vapor outlets, at least 4 vapor outlets, at least 6 vapor outlets, at least 9 vapor outlets, at least 10 vapor outlets, at least 14 vapor outlets, at least 15 vapor outlets, at least 18 vapor outlets, or at least 20 vapor outlets.

[0103] In some embodiments, the one or more vapor outlets includes at most 1 vapor outlet, at most 2 vapor outlets, at most 4 vapor outlets, at most 6 vapor outlets, at most 9 vapor outlets, at most 10 vapor outlets, at most 14 vapor outlets, at most 15 vapor outlets, at most 18 vapor outlets, or at most 20 vapor outlets.

[0104] In some embodiments, the one or more vapor outlets is in a range that contains between 1 vapor outlet and 2 vapor outlets, between 1 vapor outlet and 6 vapor outlets,Attorney Docket No. : 136048-5006-WO between 1 vapor outlet and 10 vapor outlets, between 1 vapor outlet and 14 vapor outlets, between 1 vapor outlet and 18 vapor outlets, between 1 vapor outlet and 20 vapor outlets, between 2 vapor outlets and 6 vapor outlets, between 2 vapor outlets and 9 vapor outlets, between 2 vapor outlets and 14 vapor outlets, between 2 vapor outlets and 18 vapor outlets, between 2 vapor outlets and 20 vapor outlets, between 4 vapor outlets and 9 vapor outlets, between 4 vapor outlets and 14 vapor outlets, between 4 vapor outlets and 15 vapor outlets, between 4 vapor outlets and 20 vapor outlets, between 6 vapor outlets and 9 vapor outlets, between 6 vapor outlets and 14 vapor outlets, between 6 vapor outlets and 15 vapor outlets, between 6 vapor outlets and 20 vapor outlets, between 9 vapor outlets and 10 vapor outlets, between 9 vapor outlets and 15 vapor outlets, between 9 vapor outlets and 20 vapor outlets, between 10 vapor outlets and 14 vapor outlets, between 10 vapor outlets and 18 vapor outlets, between 10 vapor outlets and 20 vapor outlets, between 14 vapor outlets and 15 vapor outlets, between 14 vapor outlets and 20 vapor outlets, between 15 vapor outlets and 18 vapor outlets, between 15 vapor outlets and 20 vapor outlets, or between 18 vapor outlets and 20 vapor outlets, inclusive.

[0105] In some embodiments, a branch angle between a distributor channel 266 of the steam recirculation manifold 260 and an intermediate channel 268 of the steam recirculation manifold 260 is allows for controlling the flow of high-pressure steam between the outlet of the compressor train and the vapor inlet of the flash vessel via the steam recirculating manifold 260. For instance, in some embodiments, the branch angle between a distributor channel 266 of the steam recirculation manifold 260 and an intermediate channel 268 of the steam recirculation manifold 260 is 90 ° or about 90 ° (e.g., 90.1 °, 89.99 °, 90.5 °, etc.). In some embodiments, the branch angle is substantially 90 °.

[0106] In some embodiments, the branch angle is at least 85 °, at least 87 °, at least 90 °, at least 92 °, at least 93 °, at least 96 °, at least 98 °, at least 100 °, at least 102 °, or at least 105 °.

[0107] In some embodiments, the branch angle is at most 85 °, at most 87 °, at most 90 °, at most 92 °, at most 93 °, at most 96 °, at most 98 °, at most 100 °, at most 102 °, or at most 105 °.

[0108] In some embodiments, the branch angle is in a range that contains between 85 ° and 87 °, between 85 ° and 92 °, between 85 ° and 96 °, between 85 ° and 98 °, between 85 ° and 102 °, between 85 ° and 105 °, between 87 ° and 92 °, between 87 ° and 93 °, between 87 ° and 98 °, between 87 ° and 102 °, between 87 ° and 105 °, between 90 ° and 93 °, between 90 ° and 98 °, between 90 ° and 100 °, between 90 ° and 105 °, between 92 ° and 93Attorney Docket No. : 136048-5006-WO°, between 92 ° and 98 °, between 92 ° and 100 °, between 92 ° and 105 °, between 93 ° and 96 °, between 93 ° and 100 °, between 93 ° and 105 °, between 96 ° and 98 °, between 96 ° and 102 °, between 96 ° and 105 °, between 98 ° and 100 °, between 98 ° and 105 °, between 100 ° and 102 °, between 100 ° and 105 °, or between 102 ° and 105 °, inclusive.

[0109] In some embodiments, the branch angle between the distributor channel 266 of the steam recirculation manifold 260 and an intermediate channel 268 of the steam recirculation manifold 260 is obtuse. For instance, in some embodiments, the branch angle is at least 90 °, at least 95 °, at least 100 °, at least 105 °, at least 110 °, at least 115 °, at least 120 °, at least 125 °, at least 130 °, at least 135 °, at least 135 °, at least 140 °, at least 145 °, at least 150 °, at least 155 °, at least 160 °, at least 165 °, at least 170 °, at least 175 °, or at least 180 °.

[0110] In some embodiments, the branch angle is at most 91 °, at most 95 °, at most 100 °, at most 105 °, at most 110 °, at most 115 °, at most 120 °, at most 125 °, at most 130 °, at most 135 °, at most 135 °, at most 140 °, at most 145 °, at most 150 °, at most 155 °, at most 160 °, at most 165 °, at most 170 °, at most 175 °, or at most 180 °.

[0111] In some embodiments, the branch angle is in a range that contains between 90 ° and 95 °, between 90 ° and 115 °, between 90 ° and 135 °, between 90 ° and 155 °, between 90 ° and 175 °, between 90 ° and 180 °, between 95 ° and 115 °, between 95 ° and 135 °, between 95 ° and 155 °, between 95 ° and 175 °, between 95 ° and 180 °, between 100 ° and 120 °, between 100 ° and 135 °, between 100 ° and 160 °, between 100 ° and 180 °, between 105 ° and 110 °, between 105 ° and 130 °, between 105 ° and 150 °, between 105 ° and 170 °, between 105 ° and 180 °, between 110 ° and 125 °, between 110 ° and 140 °, between 110 ° and 160 °, between 110 ° and 180 °, between 115 ° and 125 °, between 115 ° and 140 °, between 115 ° and 160 °, between 115 ° and 180 °, between 120 ° and 130 °, between 120 ° and 145 °, between 120 ° and 165 °, between 120 ° and 180 °, between 125 ° and 135 °, between 125 ° and 150 °, between 125 ° and 175 °, between 125 ° and 180 °, between 130 ° and 145 °, between 130 ° and 165 °, between 130 ° and 180 °, between 135 ° and 145 °, between 135 ° and 165 °, between 135 ° and 180 °, between 135 ° and 145 °, between 135 ° and 165 °, between 135 ° and 180 °, between 140 ° and 150 °, between 140 ° and 175 °, between 140 ° and 180 °, between 145 ° and 165 °, between 145 ° and 180 °, between 150 ° and 160 °, between 150 ° and 180 °, between 155 ° and 165 °, between 155 ° and 180 °, between 160 ° and 170 °, between 160 ° and 180 °, between 165 ° and 180 °, between 170 ° and 175 °, between 170 ° and 180 °, or between 175 ° and 180 °, inclusive.Attorney Docket No. : 136048-5006-WO

[0112] In some embodiments, the branch angle between the distributor channel 266 of the steam recirculation manifold and the intermediate channel 268 of the steam recirculation manifold allows for connections that simplify the layout and facilitate modular assembly of th system 104. For instance, in some embodiments, the 90° branch angle is utilized to minimize pressure losses and optimize steam flow through the steam recirculation manifold, such as to satisfy space constraint require compact arrangements. In some embodiments, the obtuse branch angle provides a more gradual transition for steam flow and potentially reducing turbulence, jet impinging, and / or erosion within the steam recirculation manifold. In some embodiments, the branch angle is chosen to accommodate specific facility layouts or to enhance the efficiency of steam distribution by allowing smoother directional changes in the piping. In some embodiments, the selection of either a 90° or obtuse branch angle depends on the desired operational characteristics, available space, and the need to balance pressure drop, flow velocity, and ease of maintenance within the steam recirculation system.

[0113] In some embodiments, the steam recirculation manifold 260 is configured to induce flow via a pressure gradient between the vapor inlet and the one or more vapor outlets of the steam recirculation manifold. By way of non-limiting example, in some embodiments, the vapor inlet receives high-pressure steam from the outlet of the compressor train and the steam recirculation manifold 260 is configured such that the pressure at the vapor inlet is greater than the pressure at each vapor outlet, generating a pressure gradient within the system 104. However, the present disclosure is not limited thereto. In some embodiments, this pressure gradient, or pressure differential, is achieved by controlling the operating conditions of the compressor train and the flash vessels, allowing high-pressure steam to naturally flow from the higher-pressure region at the manifold inlet to the lower-pressure regions at the vapor outlets. In some embodiments, the steam recirculation manifold 260 includes one or more channels having a diameter and a length, in which the diameter and / or length is configured to minimize pressure losses and maximize the efficiency of steam recirculation.

[0114] In some embodiments, the steam recirculation manifold 260 is configured to induce flow via a pressure gradient between the vapor inlet of the steam recirculation manifold and an inlet of another terminal flash vessel of the flash vessel structure, such that the pressure at the vapor inlet is higher than the pressure at the inlet of the terminal flash vessel. In some embodiments, this configuration enables high-pressure steam to be recirculated from the compressor train outlet, through the steam recirculation manifold 260, and directly into the terminal flash vessel, leveraging the pressure difference to drive the flowAttorney Docket No. : 136048-5006-WO without the need for additional pumps or mechanical devices. In some embodiments, the steam recirculation manifold 260 the pressure gradient is maintained by the relative operating pressures of the compressor train and each branch separating a flow between the distributor channel of the steam recirculation manifold 260 and a corresponding vapor inlet of the flash vessel, operational modes.

[0115] In some embodiments, a first valve 310-1 selectively controls fluid communication between the outlet of the compressor train 212 and (i) the facility (ii) and the steam recirculation manifold 260. In some embodiments, the first valve enables dynamic management of high-pressure steam distribution from the compressor 216 between the facility and the steam recirculation manifold 260, such as responsive to a demand from the system 104 by the facility. By way of non-limiting example, in some embodiments, the first valve includes multi-port control valve, such as a three-way valve, that is positioned at the junction where the compressor train outlet branches toward the facility and the steam recirculation manifold.

[0116] In some embodiments, the first valve 310-1 is configured to operate in a first position allowing at most 100 volume percent (vol%) of the high-pressure steam to flow from the outlet of the compressor train to the facility.

[0117] In some embodiments, the first position of the first value 310-1 allows at least 1 vol%, at least 5 vol%, at least 10 vol%, at least 15 vol%, at least 20 vol%, at least 25 vol%, at least 30 vol%, at least 35 vol%, at least 40 vol%, at least 50 vol%, at least 55 vol%, at least 60 vol%, at least 65 vol%, at least 70 vol%, at least 75 vol%, at least 80 vol%, at least 85 vol%, at least 90 vol%, at least 95 vol%, or at least 100 vol% of the high-pressure steam to flow from the outlet of the compressor train to the facility.

[0118] In some embodiments, the first position of the first value 310-1 allows at most 1 vol%, at most 5 vol%, at most 10 vol%, at most 15 vol%, at most 20 vol%, at most 25 vol%, at most 30 vol%, at most 35 vol%, at most 40 vol%, at most 50 vol%, at most 55 vol%, at most 60 vol%, at most 65 vol%, at most 70 vol%, at most 75 vol%, at most 80 vol%, at most 85 vol%, at most 90 vol%, at most 95 vol%, or at most 100 vol% of the high-pressure steam to flow from the outlet of the compressor train to the facility.

[0119] In some embodiments, the first position of the first value 310-1 allows a range that contains between 1 vol% and 5 vol%, between 1 vol% and 25 vol%, between 1 vol% and 50 vol%, between 1 vol% and 75 vol%, between 1 vol% and 95 vol%, between 1 vol% and 100 vol%, between 5 vol% and 25 vol%, between 5 vol% and 55 vol%, between 5 vol% and 75 vol%, between 5 vol% and 95 vol%, between 5 vol% and 100 vol%, between 10 vol% andAttorney Docket No. : 136048-5006-WO30 vol%, between 10 vol% and 55 vol%, between 10 vol% and 80 vol%, between 10 vol% and 100 vol%, between 15 vol% and 20 vol%, between 15 vol% and 40 vol%, between 15 vol% and 70 vol%, between 15 vol% and 90 vol%, between 15 vol% and 100 vol%, between 20 vol% and 35 vol%, between 20 vol% and 60 vol%, between 20 vol% and 80 vol%, between 20 vol% and 100 vol%, between 25 vol% and 35 vol%, between 25 vol% and 60 vol%, between 25 vol% and 80 vol%, between 25 vol% and 100 vol%, between 30 vol% and 40 vol%, between 30 vol% and 65 vol%, between 30 vol% and 85 vol%, between 30 vol% and 100 vol%, between 35 vol% and 50 vol%, between 35 vol% and 70 vol%, between 35 vol% and 95 vol%, between 35 vol% and 100 vol%, between 40 vol% and 65 vol%, between 40 vol% and 85 vol%, between 40 vol% and 100 vol%, between 50 vol% and 65 vol%, between 50 vol% and 85 vol%, between 50 vol% and 100 vol%, between 55 vol% and 65 vol%, between 55 vol% and 85 vol%, between 55 vol% and 100 vol%, between 60 vol% and 70 vol%, between 60 vol% and 95 vol%, between 60 vol% and 100 vol%, between 65 vol% and 85 vol%, between 65 vol% and 100 vol%, between 70 vol% and 80 vol%, between 70 vol% and 100 vol%, between 75 vol% and 85 vol%, between 75 vol% and 100 vol%, between 80 vol% and 90 vol%, between 80 vol% and 100 vol%, between 85 vol% and 100 vol%, between 90 vol% and 95 vol%, between 90 vol% and 100 vol%, or between 95 vol% and 100 vol%, inclusive, of the high-pressure steam to flow from the outlet of the compressor train to the facility.

[0120] In some embodiments, the first valve is configured to operate in a second position allowing at most 100 vol% of the high-pressure steam to flow from the outlet of the compressor train to the steam recirculation manifold.

[0121] In some embodiments, the second position of the first value 310-1 allows at least 1 vol%, at least 5 vol%, at least 10 vol%, at least 15 vol%, at least 20 vol%, at least 25 vol%, at least 30 vol%, at least 35 vol%, at least 40 vol%, at least 50 vol%, at least 55 vol%, at least 60 vol%, at least 65 vol%, at least 70 vol%, at least 75 vol%, at least 80 vol%, at least 85 vol%, at least 90 vol%, at least 95 vol%, or at least 100 vol% of the high-pressure steam to flow from the outlet of the compressor train to the steam recirculation manifold.

[0122] In some embodiments, the second position of the first value 310-1 allows at most 1 vol%, at most 5 vol%, at most 10 vol%, at most 15 vol%, at most 20 vol%, at most 25 vol%, at most 30 vol%, at most 35 vol%, at most 40 vol%, at most 50 vol%, at most 55 vol%, at most 60 vol%, at most 65 vol%, at most 70 vol%, at most 75 vol%, at most 80 vol%, at most 85 vol%, at most 90 vol%, at most 95 vol%, or at most 100 vol% of the high-pressure steam to flow from the outlet of the compressor train to the steam recirculation manifold.Attorney Docket No. : 136048-5006-WO

[0123] In some embodiments, the second position of the first value 310-1 allows a range that contains between 1 vol% and 5 vol%, between 1 vol% and 25 vol%, between 1 vol% and 50 vol%, between 1 vol% and 75 vol%, between 1 vol% and 95 vol%, between 1 vol% and 100 vol%, between 5 vol% and 25 vol%, between 5 vol% and 55 vol%, between 5 vol% and 75 vol%, between 5 vol% and 95 vol%, between 5 vol% and 100 vol%, between 10 vol% and 30 vol%, between 10 vol% and 55 vol%, between 10 vol% and 80 vol%, between 10 vol% and 100 vol%, between 15 vol% and 20 vol%, between 15 vol% and 40 vol%, between 15 vol% and 70 vol%, between 15 vol% and 90 vol%, between 15 vol% and 100 vol%, between 20 vol% and 35 vol%, between 20 vol% and 60 vol%, between 20 vol% and 80 vol%, between 20 vol% and 100 vol%, between 25 vol% and 35 vol%, between 25 vol% and 60 vol%, between 25 vol% and 80 vol%, between 25 vol% and 100 vol%, between 30 vol% and 40 vol%, between 30 vol% and 65 vol%, between 30 vol% and 85 vol%, between 30 vol% and 100 vol%, between 35 vol% and 50 vol%, between 35 vol% and 70 vol%, between 35 vol% and 95 vol%, between 35 vol% and 100 vol%, between 40 vol% and 65 vol%, between 40 vol% and 85 vol%, between 40 vol% and 100 vol%, between 50 vol% and 65 vol%, between 50 vol% and 85 vol%, between 50 vol% and 100 vol%, between 55 vol% and 65 vol%, between 55 vol% and 85 vol%, between 55 vol% and 100 vol%, between 60 vol% and 70 vol%, between 60 vol% and 95 vol%, between 60 vol% and 100 vol%, between 65 vol% and 85 vol%, between 65 vol% and 100 vol%, between 70 vol% and 80 vol%, between 70 vol% and 100 vol%, between 75 vol% and 85 vol%, between 75 vol% and 100 vol%, between 80 vol% and 90 vol%, between 80 vol% and 100 vol%, between 85 vol% and 100 vol%, between 90 vol% and 95 vol%, between 90 vol% and 100 vol%, or between 95 vol% and 100 vol%, inclusive, of the high-pressure steam to flow from the outlet of the compressor train to the steam recirculation manifold.

[0124] In some embodiments, the first valve is configured to operate in a third position allowing less than 100 vol% of the high-pressure steam to flow to either the facility or the steam recirculation manifold.

[0125] In some embodiments, the third position of the first value 310-1 allows at least 1 vol%, at least 5 vol%, at least 10 vol%, at least 15 vol%, at least 20 vol%, at least 25 vol%, at least 30 vol%, at least 35 vol%, at least 40 vol%, at least 50 vol%, at least 55 vol%, at least 60 vol%, at least 65 vol%, at least 70 vol%, at least 75 vol%, at least 80 vol%, at least 85 vol%, at least 90 vol%, at least 95 vol%, or at least 100 vol% of the high-pressure steam to flow to either the facility or the steam recirculation manifold.Attorney Docket No. : 136048-5006-WO

[0126] In some embodiments, the third position of the first value 310-1 allows at most 1 vol%, at most 5 vol%, at most 10 vol%, at most 15 vol%, at most 20 vol%, at most 25 vol%, at most 30 vol%, at most 35 vol%, at most 40 vol%, at most 50 vol%, at most 55 vol%, at most 60 vol%, at most 65 vol%, at most 70 vol%, at most 75 vol%, at most 80 vol%, at most 85 vol%, at most 90 vol%, at most 95 vol%, or at most 100 vol% of the high-pressure steam to flow to either the facility or the steam recirculation manifold.

[0127] In some embodiments, the third position of the first value 310-1 allows a range that contains between 1 vol% and 5 vol%, between 1 vol% and 25 vol%, between 1 vol% and 50 vol%, between 1 vol% and 75 vol%, between 1 vol% and 95 vol%, between 1 vol% and 100 vol%, between 5 vol% and 25 vol%, between 5 vol% and 55 vol%, between 5 vol% and 75 vol%, between 5 vol% and 95 vol%, between 5 vol% and 100 vol%, between 10 vol% and 30 vol%, between 10 vol% and 55 vol%, between 10 vol% and 80 vol%, between 10 vol% and 100 vol%, between 15 vol% and 20 vol%, between 15 vol% and 40 vol%, between 15 vol% and 70 vol%, between 15 vol% and 90 vol%, between 15 vol% and 100 vol%, between 20 vol% and 35 vol%, between 20 vol% and 60 vol%, between 20 vol% and 80 vol%, between 20 vol% and 100 vol%, between 25 vol% and 35 vol%, between 25 vol% and 60 vol%, between 25 vol% and 80 vol%, between 25 vol% and 100 vol%, between 30 vol% and 40 vol%, between 30 vol% and 65 vol%, between 30 vol% and 85 vol%, between 30 vol% and 100 vol%, between 35 vol% and 50 vol%, between 35 vol% and 70 vol%, between 35 vol% and 95 vol%, between 35 vol% and 100 vol%, between 40 vol% and 65 vol%, between 40 vol% and 85 vol%, between 40 vol% and 100 vol%, between 50 vol% and 65 vol%, between 50 vol% and 85 vol%, between 50 vol% and 100 vol%, between 55 vol% and 65 vol%, between 55 vol% and 85 vol%, between 55 vol% and 100 vol%, between 60 vol% and 70 vol%, between 60 vol% and 95 vol%, between 60 vol% and 100 vol%, between 65 vol% and 85 vol%, between 65 vol% and 100 vol%, between 70 vol% and 80 vol%, between 70 vol% and 100 vol%, between 75 vol% and 85 vol%, between 75 vol% and 100 vol%, between 80 vol% and 90 vol%, between 80 vol% and 100 vol%, between 85 vol% and 100 vol%, between 90 vol% and 95 vol%, between 90 vol% and 100 vol%, or between 95 vol% and 100 vol%, inclusive, of the high-pressure steam to flow to either the facility or the steam recirculation manifold.

[0128] In some embodiments, the system 104 further includes a controller electronically coupled to the first valve and configured to modify a position of the first valve between at least two positions (e.g., between the first position and the second position, between the first position and the third position, between the second position and the thirdAttorney Docket No. : 136048-5006-WO position, etc. . In some embodiments, rather than configuring the first valve 310-1 to be positionable among the first, second, and / or third positions, to proportion flow between the facility and the steam recirculation manifold 260, the flow is apportioned using two valves 310 arranged in series and / or parallel flowpaths downstream of the compressor train. In some embodiments, the first valve 310-1 is disposed between the outlet of the compressor train to the facility supply header, such as being configured to meter or isolate flow delivered to the facility. In some embodiments, a third valve 310-3 is disposed between the outlet of the compressor train and the vapor inlet of the steam recirculation manifold 260 and is configured to meter or isolate flow received into the steam recirculation manifold 260.

[0129] In some embodiments, the first valve 310-1 is actuated electronically or pneumatically, allowing for precise adjustment of its position to direct steam flow to the facility, to the steam recirculation manifold, or to both destinations in varying proportions. In some embodiments, the first valve 310-1 is integrated with a controller 906 that receives input from pressure, flow, and / or or resource consumption sensors 982, enabling automated operation based on real-time system demands and process conditions. In some embodiments, the selective control of the first valve 310-1 provided by the controller 906 allows the system 104 to operate in multiple modes, such as full steam delivery to the facility during peak demand, full recirculation for startup or closed-loop operation, or partial diversion to balance facility supply and recirculation needs.

[0130] In some embodiments, a second valve 310-2 selectively controls fluid communication between the distributor channel 266 of the steam recirculation manifold and the intermediate channel 268 of the steam recirculation manifold. In some embodiments, the second valve 310-2 enables precise regulation of steam flow through a specific branch of flow associated with the respective flash vessel. In some embodiments, the selective control provided by the second valve 310-1 allows the system 104 to isolate and / or control individual flash vessels for maintenance, adjust steam recirculation rates for anti-surge protection, and / or optimize energy efficiency by controlling flow of high-pressure steam received to each stage of the flash vessel structure 202.

[0131] In some embodiments, the second valve 310-2 is configured to operate in a first position allowing at most 100 volume percent (vol%) of the high-pressure steam to flow from the distributor channel 266 to the intermediate channel 268.

[0132] In some embodiments, the first position of the second valve 310-2 allows at least 1 vol%, at least 5 vol%, at least 10 vol%, at least 15 vol%, at least 20 vol%, at least 25 vol%, at least 30 vol%, at least 35 vol%, at least 40 vol%, at least 50 vol%, at least 55 vol%,Attorney Docket No. : 136048-5006-WO at least 60 vol%, at least 65 vol%, at least 70 vol%, at least 75 vol%, at least 80 vol%, at least 85 vol%, at least 90 vol%, at least 95 vol%, or at least 100 vol% of the high-pressure steam to flow from the distributor channel 266 to the intermediate channel 268.

[0133] In some embodiments, the first position of the second valve 310-2 allows at most 1 vol%, at most 5 vol%, at most 10 vol%, at most 15 vol%, at most 20 vol%, at most 25 vol%, at most 30 vol%, at most 35 vol%, at most 40 vol%, at most 50 vol%, at most 55 vol%, at most 60 vol%, at most 65 vol%, at most 70 vol%, at most 75 vol%, at most 80 vol%, at most 85 vol%, at most 90 vol%, at most 95 vol%, or at most 100 vol% of the high-pressure steam to flow from the distributor channel 266 to the intermediate channel 268.

[0134] In some embodiments, the first position of the second valve 310-2 allows a range that contains between 1 vol% and 5 vol%, between 1 vol% and 25 vol%, between 1 vol% and 50 vol%, between 1 vol% and 75 vol%, between 1 vol% and 95 vol%, between 1 vol% and 100 vol%, between 5 vol% and 25 vol%, between 5 vol% and 55 vol%, between 5 vol% and 75 vol%, between 5 vol% and 95 vol%, between 5 vol% and 100 vol%, between 10 vol% and 30 vol%, between 10 vol% and 55 vol%, between 10 vol% and 80 vol%, between 10 vol% and 100 vol%, between 15 vol% and 20 vol%, between 15 vol% and 40 vol%, between 15 vol% and 70 vol%, between 15 vol% and 90 vol%, between 15 vol% and 100 vol%, between 20 vol% and 35 vol%, between 20 vol% and 60 vol%, between 20 vol% and 80 vol%, between 20 vol% and 100 vol%, between 25 vol% and 35 vol%, between 25 vol% and 60 vol%, between 25 vol% and 80 vol%, between 25 vol% and 100 vol%, between 30 vol% and 40 vol%, between 30 vol% and 65 vol%, between 30 vol% and 85 vol%, between 30 vol% and 100 vol%, between 35 vol% and 50 vol%, between 35 vol% and 70 vol%, between 35 vol% and 95 vol%, between 35 vol% and 100 vol%, between 40 vol% and 65 vol%, between 40 vol% and 85 vol%, between 40 vol% and 100 vol%, between 50 vol% and 65 vol%, between 50 vol% and 85 vol%, between 50 vol% and 100 vol%, between 55 vol% and 65 vol%, between 55 vol% and 85 vol%, between 55 vol% and 100 vol%, between 60 vol% and 70 vol%, between 60 vol% and 95 vol%, between 60 vol% and 100 vol%, between 65 vol% and 85 vol%, between 65 vol% and 100 vol%, between 70 vol% and 80 vol%, between 70 vol% and 100 vol%, between 75 vol% and 85 vol%, between 75 vol% and 100 vol%, between 80 vol% and 90 vol%, between 80 vol% and 100 vol%, between 85 vol% and 100 vol%, between 90 vol% and 95 vol%, or between 95 vol% and 100 vol%, inclusive, of the high-pressure steam to flow from the distributor channel 266 to the intermediate channel 268.Attorney Docket No. : 136048-5006-WO

[0135] In some embodiments, the second valve 310-2 is configured to operate in a second position allowing at most 100 vol% of the high-pressure steam to flow from the distributor channel 266 to the intermediate channel 268.

[0136] In some embodiments, the second position of the second valve 310-2 allows at least 1 vol%, at least 5 vol%, at least 10 vol%, at least 15 vol%, at least 20 vol%, at least 25 vol%, at least 30 vol%, at least 35 vol%, at least 40 vol%, at least 50 vol%, at least 55 vol%, at least 60 vol%, at least 65 vol%, at least 70 vol%, at least 75 vol%, at least 80 vol%, at least 85 vol%, at least 90 vol%, at least 95 vol%, or at least 100 vol% of the high-pressure steam to flow from the distributor channel 266 to the intermediate channel 268.

[0137] In some embodiments, the second position of the second valve 310-2 allows at most 1 vol%, at most 5 vol%, at most 10 vol%, at most 15 vol%, at most 20 vol%, at most 25 vol%, at most 30 vol%, at most 35 vol%, at most 40 vol%, at most 50 vol%, at most 55 vol%, at most 60 vol%, at most 65 vol%, at most 70 vol%, at most 75 vol%, at most 80 vol%, at most 85 vol%, at most 90 vol%, at most 95 vol%, or at most 100 vol% of the high-pressure steam to flow from the distributor channel 266 to the intermediate channel 268.

[0138] In some embodiments, the second position of the second valve 310-2 allows a range that contains between 1 vol% and 5 vol%, between 1 vol% and 25 vol%, between 1 vol% and 50 vol%, between 1 vol% and 75 vol%, between 1 vol% and 95 vol%, between 1 vol% and 100 vol%, between 5 vol% and 25 vol%, between 5 vol% and 55 vol%, between 5 vol% and 75 vol%, between 5 vol% and 95 vol%, between 5 vol% and 100 vol%, between 10 vol% and 30 vol%, between 10 vol% and 55 vol%, between 10 vol% and 80 vol%, between 10 vol% and 100 vol%, between 15 vol% and 20 vol%, between 15 vol% and 40 vol%, between 15 vol% and 70 vol%, between 15 vol% and 90 vol%, between 15 vol% and 100 vol%, between 20 vol% and 35 vol%, between 20 vol% and 60 vol%, between 20 vol% and 80 vol%, between 20 vol% and 100 vol%, between 25 vol% and 35 vol%, between 25 vol% and 60 vol%, between 25 vol% and 80 vol%, between 25 vol% and 100 vol%, between 30 vol% and 40 vol%, between 30 vol% and 65 vol%, between 30 vol% and 85 vol%, between 30 vol% and 100 vol%, between 35 vol% and 50 vol%, between 35 vol% and 70 vol%, between 35 vol% and 95 vol%, between 35 vol% and 100 vol%, between 40 vol% and 65 vol%, between 40 vol% and 85 vol%, between 40 vol% and 100 vol%, between 50 vol% and 65 vol%, between 50 vol% and 85 vol%, between 50 vol% and 100 vol%, between 55 vol% and 65 vol%, between 55 vol% and 85 vol%, between 55 vol% and 100 vol%, between 60 vol% and 70 vol%, between 60 vol% and 95 vol%, between 60 vol% and 100 vol%, between 65 vol% and 85 vol%, between 65 vol% and 100 vol%, between 70 vol% and 80 vol%,Attorney Docket No. : 136048-5006-WO between 70 vol% and 100 vol%, between 75 vol% and 85 vol%, between 75 vol% and 100 vol%, between 80 vol% and 90 vol%, between 80 vol% and 100 vol%, between 85 vol% and 100 vol%, between 90 vol% and 95 vol%, between 90 vol% and 100 vol%, or between 95 vol% and 100 vol%, inclusive, of the high-pressure steam to flow from the distributor channel 266 to the intermediate channel 268.

[0139] In some embodiments, the second valve is configured to operate in a third position allowing less than 100 vol% of the high-pressure steam to flow from the distributor channel 266 to the intermediate channel 268.

[0140] In some embodiments, the third position of the second valve 310-2 allows at least 1 vol%, at least 5 vol%, at least 10 vol%, at least 15 vol%, at least 20 vol%, at least 25 vol%, at least 30 vol%, at least 35 vol%, at least 40 vol%, at least 50 vol%, at least 55 vol%, at least 60 vol%, at least 65 vol%, at least 70 vol%, at least 75 vol%, at least 80 vol%, at least 85 vol%, at least 90 vol%, at least 95 vol%, or at least 100 vol% of the high-pressure steam to flow from the distributor channel 266 to the intermediate channel 268..

[0141] In some embodiments, the third position of the second valve 310-2 allows at most 1 vol%, at most 5 vol%, at most 10 vol%, at most 15 vol%, at most 20 vol%, at most 25 vol%, at most 30 vol%, at most 35 vol%, at most 40 vol%, at most 50 vol%, at most 55 vol%, at most 60 vol%, at most 65 vol%, at most 70 vol%, at most 75 vol%, at most 80 vol%, at most 85 vol%, at most 90 vol%, at most 95 vol%, or at most 100 vol% of the high-pressure steam to flow from the distributor channel 266 to the intermediate channel 268..

[0142] In some embodiments, the third position of the second valve 310-2 allows a range that contains between 1 vol% and 5 vol%, between 1 vol% and 25 vol%, between 1 vol% and 50 vol%, between 1 vol% and 75 vol%, between 1 vol% and 95 vol%, between 1 vol% and 100 vol%, between 5 vol% and 25 vol%, between 5 vol% and 55 vol%, between 5 vol% and 75 vol%, between 5 vol% and 95 vol%, between 5 vol% and 100 vol%, between 10 vol% and 30 vol%, between 10 vol% and 55 vol%, between 10 vol% and 80 vol%, between 10 vol% and 100 vol%, between 15 vol% and 20 vol%, between 15 vol% and 40 vol%, between 15 vol% and 70 vol%, between 15 vol% and 90 vol%, between 15 vol% and 100 vol%, between 20 vol% and 35 vol%, between 20 vol% and 60 vol%, between 20 vol% and 80 vol%, between 20 vol% and 100 vol%, between 25 vol% and 35 vol%, between 25 vol% and 60 vol%, between 25 vol% and 80 vol%, between 25 vol% and 100 vol%, between 30 vol% and 40 vol%, between 30 vol% and 65 vol%, between 30 vol% and 85 vol%, between 30 vol% and 100 vol%, between 35 vol% and 50 vol%, between 35 vol% and 70 vol%, between 35 vol% and 95 vol%, between 35 vol% and 100 vol%, between 40 vol% and 65Attorney Docket No. : 136048-5006-WO vol%, between 40 vol% and 85 vol%, between 40 vol% and 100 vol%, between 50 vol% and 65 vol%, between 50 vol% and 85 vol%, between 50 vol% and 100 vol%, between 55 vol% and 65 vol%, between 55 vol% and 85 vol%, between 55 vol% and 100 vol%, between 60 vol% and 70 vol%, between 60 vol% and 95 vol%, between 60 vol% and 100 vol%, between 65 vol% and 85 vol%, between 65 vol% and 100 vol%, between 70 vol% and 80 vol%, between 70 vol% and 100 vol%, between 75 vol% and 85 vol%, between 75 vol% and 100 vol%, between 80 vol% and 90 vol%, between 80 vol% and 100 vol%, between 85 vol% and 100 vol%, between 90 vol% and 95 vol%, between 90 vol% and 100 vol%, or between 95 vol% and 100 vol%, inclusive, of the high-pressure steam to flow from the distributor channel 266 to the intermediate channel 268.

[0143] In some embodiments, the system further includes a controller 906 electronically coupled to the second valve 310-2. In some embodiments, the controller 906 is configured to modify a position of the second valve 310-2 between at least two positions. In some embodiments, the second valve 310-2 is actuated electronically, pneumatically, or manually, allowing for real-time adjustment of the valve opening to increase, decrease, or completely shut off steam flow to the flash vessel as required by process conditions. In some embodiments, the second valve 310-2 is integrated with a local or central controller 906 that receives input from pressure, flow, and / or temperature sensors 982 positioned along the distributor channel 266 and / or the intermediate channel 268, enabling automated feedback control to maintain optimal operating parameters within the flash vessel. In some embodiments, the selective control provided by the second valve allows the system to isolate individual flash vessels for maintenance, adjust steam recirculation rates for anti-surge protection, and / or optimize energy efficiency by tailoring steam delivery to each stage of the flash vessel structure. In some embodiments, the controller 906 is configured to respond to changes in facility demand, flash vessel pressure, or system safety protocols and control the second valve 310-2 based on the changes, ensuring reliable and flexible operation of the steam recirculation manifold and the system.

[0144] In some embodiments, a respective valve (e.g. fourth valve 310-4, fifth valve 310-5, and / or sixth valve 310-6 of Figures 3-9, etc.) performs the same function as the second valve 310-2, but respectively for a corresponding intermediate channel and vapor inlet of a corresponding flash vessel in the flash vessel structure 202. In some embodiments, each of the fourth valve 310-4, the fifth valve 310-5, and the sixth valve 310-6 is disposed between a distributor channel 266 of the steam recirculation manifold and the corresponding intermediate channel 268 that feeds a vapor inlet of a respective flash vessel, and each valveAttorney Docket No. : 136048-5006-WO selectively meters or isolates high-pressure steam flow from the distributor channel 266 into the corresponding intermediate channel 2678 to control recirculation into the associated flash vessel. However, the present disclosure is not limited thereto.

[0145] In some embodiments, the fourth valve 310-4 regulates flow into a first intermediate channel coupled to a first flash vessel vapor inlet, the fifth valve 310-5 regulates flow into a second intermediate channel coupled to a second flash vessel vapor inlet, and the sixth valve 310-6 regulates flow into a third intermediate channel coupled to a third flash vessel vapor inlet. In some embodiments, each valve is independently actuated to achieve one or more operating states including a fully closed isolation state, a commanded throttling state allowing up to 100 vol% of the available recirculation steam to enter its respective intermediate channel, and a split-flow state in which less than 100 vol% is admitted according to a control law that coordinates recirculation distribution among multiple flash vessels.

[0146] In some embodiments, the controller generates independent actuator commands to the fourth valve 310-4, the fifth valve 310-5, and the sixth valve 310-6 based on pressure, temperature, and flow signals associated with the respective intermediate channels and flash vessel vapor inlets, thereby maintaining target pressures and flow rates within each flash vessel stage. In some embodiments, the valves 310 implement equal-percentage, linear, or quick-opening trims selected to optimize controllability for the dynamic response of the corresponding flash vessel, and each valve 310 incorporates position feedback and, optionally, upstream / downstream pressure sensing to support diagnostics and adaptive regulation.

[0147] In some embodiments, fail-safe behavior is implemented such that, upon loss of control power or detection of a fault condition at a given stage, the corresponding valve among the fourth valve 310-4, the fifth valve 310-5, and the sixth valve 310-6 fails closed to prevent uncontrolled admission of steam into its intermediate channel while the remaining valves continue regulated operation to sustain overall system stability. In some embodiments, during startup and shutdown sequences, the controller 906 staggers opening and closing of the fourth valve 310-4, the fifth valve 310-5, and the sixth valve 310-6 to purge non-condensables, establish recirculation paths, and avoid transient pressure excursions in the flash vessel structure. However, the present disclosure is not limited thereto.

[0148] In some embodiments, by providing stage-specific recirculation control via the fourth valve 310-4, the fifth valve 310-5, and the sixth valve 310-6 with the same functional role as the second valve 310-2, the system achieves granular distribution of recirculatedAttorney Docket No. : 136048-5006-WO steam to each flash vessel, improves pressure and flow uniformity across the flash vessel structure, and enhances anti-surge robustness and operational flexibility without relying on a single common throttling element.

[0149] In some embodiments, the system further includes a first sensor 982-1 configured to detect a pressure associated with the compressor train, and the controller 906 that is electrically coupled to the first sensor and the first valve and / or the second valve is further configured to maintain the pressure of the compressor train. By way of non-limiting example, in some embodiments, the first sensor 982 detects a pressure associated with the compressor train, and the controller 906 receives this pressure data and adjusts the first valve 310-1 and / or the second valve 310-2 to maintain the desired pressure within the compressor train. In some embodiments, by continuously monitoring and controlling the pressure, the controller 906 prevents overpressure or under pressure conditions, which increases system reliability and operational safety. In some embodiments, the controller 906 also allows for alternative flow path control, such as responding to setpoints, process limits, or manual override for maintenance.

[0150] In some embodiments, the system further includes a second sensor 982-2 configured to detect a pressure associated with the flash vessel structure, and the controller 906 that is electrically coupled to the second sensor and the second valve is further configured to maintain the pressure of the flash vessel structure. In some embodiments, the second sensor 982 detects a pressure associated with the flash vessel structure, and the controller 906 receives this data and modulates the second valve to maintain the optimal pressure profile across the flash vessel stages. The controller 906 ensures consistent steam generation and separation, enhancing process stability and product quality. The controller 906 also provides flexibility to maintain pressure within a range or follow a pressure ramp for startup or shutdown.

[0151] In some embodiments, the system further includes a third sensor configured to detect a pressure associated with the steam recirculation manifold, and the controller that is electrically coupled to the third sensor and both (i) the first valve and (ii) the second valve and is further configured to maintain the pressure of the steam recirculation manifold. In some embodiments, the third sensor 982-3 detects a pressure associated with the steam recirculation manifold, and the controller 906 receives this data and coordinates the operation of both the first valve and the second valve to keep the manifold pressure within safe and efficient limits. The controller 906 enables effective steam recirculation and system protection by responding rapidly to pressure surges or drops, reducing downtime andAttorney Docket No. : 136048-5006-WO maintenance costs. The controller 906 also supports adaptive control strategies based on process demand or facility operating modes.

[0152] In some embodiments, the system further includes a fourth sensor configured to detect a flow rate associated with the compressor train, and the controller that is electrically coupled to the fourth sensor and the first valve and / or the second valve is further configured to maintain the flow rate of the compressor train. In some embodiments, the fourth sensor 982-4 detects a flow rate associated with the compressor train, and the controller 906 receives this flow data and adjusts the first valve and / or the second valve to deliver the required steam volume for process needs. The controller 906 improves energy utilization and system responsiveness by maintaining the correct flow rate and preventing inefficiencies or equipment stress. The controller 906 also allows for alternatives such as maintaining minimum or maximum flow rates or following a flow profile for batch or continuous operations.

[0153] In some embodiments, the system further includes a fifth sensor configured to detect a flow rate associated with the flash vessel structure, and the controller that is electrically coupled to the fifth sensor and the second valve is further configured to maintain the flow rate of the flash vessel structure. In some embodiments, the fifth sensor 982-5 detects a flow rate associated with the flash vessel structure, and the controller 906 receives this data and regulates the second valve to optimize steam and condensate flow through the flash vessels. The controller 906 enhances throughput and process control by preventing bottlenecks or flooding and maintaining consistent flow rates. The controller 906 also adjusts flow based on downstream process requirements or target ranges.

[0154] In some embodiments, the system further includes a sixth sensor configured to detect a flow rate associated with the steam recirculation manifold, and the controller that is electrically coupled to the sixth sensor and both (i) the first valve and (ii) the second valve and is further configured to maintain the flow rate of the steam recirculation manifold. In some embodiments, the sixth sensor 982-6 detects a flow rate associated with the steam recirculation manifold, and the controller 906 receives this data and balances the operation of the first valve and the second valve to ensure efficient recirculated steam flow. The controller 906 increases system flexibility and reliability by preventing steam starvation or excess recirculation and optimizing flow for energy savings or facility load changes.

[0155] In some embodiments, the system further includes a seventh sensor configured to detect a resource consumption associated with the compressor train, and the controller that is electrically coupled to the seventh sensor and the first valve and / or the second valve isAttorney Docket No. : 136048-5006-WO further configured to maintain the resource consumption of the compressor train. In some embodiments, the seventh sensor 982-7 detects a resource consumption associated with the compressor train, and the controller 906 receives this data and optimizes the operation of the first valve and / or the second valve to reduce energy usage and operational costs while maintaining required performance. The controller 906 supports sustainability and cost management by continuously monitoring and controlling resource consumption and operating in energy-saving modes or prioritizing resource allocation.

[0156] In some embodiments, the seventh sensor is configured to detect resource consumption of the compressor train as electrical power use. For instance, in some embodiments, each compressor of the compressor train includes the seventh sensor, which allows for detecting resource consumption on a per-compressor basis, including one or more of real-time active power, apparent power, current, voltage, frequency, and / or power factor as measured at each compressor motor drive, in some embodiments, a subset of compressors of the compressor train, which is less than all compressors, includes the seventh sensor. In some embodiments, the controller is electrically coupled to the seventh sensor and computes stagespecific shaft power by correcting the measured electrical power for variable-frequency drive and motor efficiencies, and then combines the shaft power estimate with measured temperatures and pressures at the inlet and outlet of the corresponding compressor stage to infer an expected mass flow and volume flow using compressor performance correlations or stored compressor maps. In some embodiments, the controller determines a desired flow for the stage based on surge avoidance criteria, a target surge margin, and a commanded operating point for the compressor train, and compares the expected flow to the desired flow to calculate a flow error and a surge-margin error. In some embodiments, responsive to a positive flow deficit or a diminishing surge margin, the controller modifies valve positions by actuating the first valve and / or the second valve to increase flow through the affected stage, including opening an anti-surge or recirculation branch to raise stage throughput while maintaining the train discharge pressure constraints. In some embodiments, the controller applies rate limits, hysteresis, and rolling averages to the power-derived flow estimates to avoid control chatter, and optionally blends the power-based estimator with any available direct flow indication for calibration and drift correction, thereby maintaining the resource consumption of the compressor train within commanded bounds while preserving sufficient flow to avoid surge.

[0157] In some embodiments, the seventh sensor is associated with a single compressor in the compressor train and the controller uses that compressor’s power,Attorney Docket No. : 136048-5006-WO temperature, and pressure data to estimate stage flow and adjust only that stage’s associated valve to raise or hold flow as needed. In some embodiments, the seventh sensor is associated on a subset of compressors and the controller computed per-stage flow estimates for the subset and modified only the corresponding subset of valves while maintaining default or schedule-based positions on non-instrumented stages. In some embodiments, the seventh sensor was installed on all compressors and the controller generated a complete set of per- stage flow estimates and individually adjusted each stage’s recirculation, bypass, or inlet valve to meet desired minimum flow targets and surge margin criteria. In some embodiments, when the instrumented subset changed over time due to service, commissioning, or expansion, the controller automatically reassigned sensor-to-stage mappings and limited valve adjustments to the newly instrumented subset while leaving non-instrumented stages unchanged. In some embodiments, the controller optionally propagated conservative adjustments to immediately adjacent non-instrumented stages based on the nearest instrumented stage data to maintain uniform train stability until direct measurements became available.

[0158] In some embodiments, the system further includes an eighth sensor 982-8 configured to detect a resource consumption associated with the flash vessel structure, and the controller that is electrically coupled to the eighth sensor 982-8 and the second valve is further configured to maintain the resource consumption of the flash vessel structure. In some embodiments, the eighth sensor 982-8 detects a resource consumption associated with the flash vessel structure, and the controller 906 receives this data and adjusts steam and water flows through the second valve to minimize resource waste and improve process efficiency. The controller 906 supports operational sustainability and regulatory compliance by maintaining resource consumption within budgeted limits or responding to process efficiency targets.

[0159] In some embodiments, the system further includes a ninth sensor 982-9 configured to detect a resource consumption rate associated with the steam recirculation manifold, and the controller that is electrically coupled to the ninth sensor 982-9 and both (i) the first valve and (ii) the second valve and is further configured to maintain the resource consumption of the steam recirculation manifold. In some embodiments, the ninth sensor 982-9 detects a resource consumption rate associated with the steam recirculation manifold, and the controller 906 receives this data and optimizes the operation of both the first valve and the second valve to reduce unnecessary steam usage and support overall system efficiency. The controller 906 enhances process economics and environmental performanceAttorney Docket No. : 136048-5006-WO by adjusting recirculation rates based on facility demand, process optimization goals, or external resource constraints.

[0160] In some embodiments, a seventh valve 310-7 is disposed along a channel from a boiler positioned between the outlet of the compressor train 212 and the facility and is configured to control supplemental steam flow from the boiler into the facility supply header. In some embodiments, the seventh valve 310-7 meters or isolates boiler-derived steam to maintain a target facility pressure or flow when compressor train discharge is insufficient or during transient events, and coordinates with the first and third valves to balance boiler contribution, compressor discharge, and recirculation.

[0161] In some embodiments, a pitch of the distributor channel 266 is 0° or substantially 0°. In some embodiments, the pitch of the intermediate channel 268 is 0° or substantially 0°. In some embodiments, this pitch of the of the distributor channel and / or the intermediate channel allows for maintaining a horizontally oriented flow path that supports modular integration, fixed elevation interfaces, and / or consistent branch locations without cumulative height changes over long distances. In some embodiments, this pitch provides uniform elevation to minimize installation complexity, preserve standardized drip-leg and instrument set points, and / or enable pressure-driven conveyance of vapor and condensate independent of gravity-induced gradients. However, the present disclosure is not limited thereto.

[0162] In some embodiments, the system further includes a drain manifold 320 configured to receive liquid condensate from a steam recirculation manifold 260 and to collect, route, and / or discharge the liquid condensate to a designated recovery or return point. In some embodiments, the drain manifold 320 is positioned beneath the steam recirculation manifold 260 within a modular pipe rack to facilitate gravity-assisted capture of condensate via drip legs and traps, and the drain manifold 320 is connected to multiple branch take-offs that intercept condensed liquid at predetermined intervals along the steam recirculation manifold 260. In some embodiments, the drain manifold 320 is sized to accommodate expected two-phase flow regimes and incorporates provisions such as separators, traps, and check valves to prevent live steam from entering the drain manifold 320 while ensuring continuous removal of accumulated condensate from the steam recirculation manifold 260.

[0163] In some embodiments, the drain manifold 320 includes at least one channel 322 fluidly coupled between a reservoir 334 of the drain manifold 320 and a distributor channel 266 and / or an intermediate channel 268 to transfer collected condensate from the steam recirculation manifold 260 into the drain manifold 320 and onward into the reservoirAttorney Docket No. : 136048-5006-WO324. In some embodiments, the at least one channel 322 is arranged as a drip leg with a steam trap or metering device to control condensate flow while minimizing steam carryover, and the reservoir 324 provides surge capacity and level control for intermittent or transient condensate loads. In some embodiments, the at least one channel 322 is configured to connect to the distributor channel 266 and the intermediate channel 268 at standardized branch locations to maintain modularity across the system, and the reservoir 324 is instrumented with level sensing and isolation valves to permit controlled discharge or return of condensate to a designated process loop. In some embodiments, the drain manifold 320, the at least one channel 322, the reservoir 324, the distributor channel 266, and / or the intermediate channel 268 are coordinated under a controller 906 to maintain target pressures and / or prevent backflow, ensuring reliable condensate management across varying operating conditions.

[0164] In some embodiments, the at least one channel 322 of drain manifold 320 includes a one-to-many relationship with the intermediate channel 268 of the flash vessel structure 202.

[0165] In some embodiments, the at least one channel 322 of drain manifold 320 includes a single channel. In some embodiments, the at least one channel of drain manifold includes at most 20 channels.

[0166] In some embodiments, the at least one channel 322 of drain manifold 320 includes at least 1 channel, at least 2 channels, at least 4 channels, at least 6 channels, at least 9 channels, at least 10 channels, at least 14 channels, at least 15 channels, at least 18 channels, or at least 20 channels.

[0167] In some embodiments, the at least one channel of drain manifold includes at most 1 channel, at most 2 channels, at most 4 channels, at most 6 channels, at most 9 channels, at most 10 channels, at most 14 channels, at most 15 channels, at most 18 channels, or at most 20 channels.

[0168] In some embodiments, the at least one channel of drain manifold is in a range that contains between 1 channel and 2 channels, between 1 channel and 6 channels, between 1 channel and 10 channels, between 1 channel and 14 channels, between 1 channel and 18 channels, between 1 channel and 20 channels, between 2 channels and 6 channels, between 2 channels and 9 channels, between 2 channels and 14 channels, between 2 channels and 18 channels, between 2 channels and 20 channels, between 4 channels and 9 channels, between 4 channels and 14 channels, between 4 channels and 15 channels, between 4 channels and 20 channels, between 6 channels and 9 channels, between 6 channels and 14 channels, between 6 channels and 15 channels, between 6 channels and 20 channels, between 9 channels and 10Attorney Docket No. : 136048-5006-WO channels, between 9 channels and 15 channels, between 9 channels and 20 channels, between 10 channels and 14 channels, between 10 channels and 18 channels, between 10 channels and 20 channels, between 14 channels and 15 channels, between 14 channels and 20 channels, between 15 channels and 18 channels, between 15 channels and 20 channels, or between 18 channels and 20 channels, inclusive.

[0169] Referring to Figures 5-9, in some embodiments, the waste heat recovery system is implemented in alternative configurations that adjust valve placement, recirculation injection locations, and steam sources while preserving the functional relationships between the flash vessel train, the compressor train, and the steam recirculation manifold. In some embodiments, Figure 5 illustrates a configuration where a valve downstream of the final compressor discharge is omitted, with the outlet feeding the facility and the recirculation header routing discharge steam upstream to flash vessel inlets and / or compressor suction connections under the remaining valves. In some embodiments, Figure 6 depicts a configuration that provides recirculation injection into the flash vessels while interstage branches serve upstream points, concentrating injection at vessel interfaces. In some embodiments, Figure 7 shows a configuration where an alternate steam source supplies the recirculation header through a controlled valve, distributing steam toward upstream injection points while the facility outlet remains valve-controlled. In some embodiments, Figure 8 illustrates a configuration where stages one and three receive recirculation steam injection, the flash vessel train delivers vapor to the compressor train, and selective injection supports surge margin at targeted stages. In some embodiments, Figure 9 depicts a configuration with three steam injection points positioned immediately upstream of compressor inlets, enabling local volume flow enhancement at suction connections, coordinated metering by the manifold and valves, and reduced flashing complexity within the vessels.

[0170] Figure 10 is a block diagram illustrating an example computer system 900 that is applied in a high-pressure steam production heat pump system, in accordance with some embodiments. In the present disclosure, unless expressly stated otherwise, descriptions of devices and systems will include implementations of one or more computers. For instance, and for purposes of illustration in Figure 10, a computer system 900 is represented as single device that includes all the functionality of the computer system 900. However, the present disclosure is not limited thereto. For instance, the functionality of the computer system 900 may be spread across any number of networked computers and / or reside on each of several networked computers and / or by hosted on one or more virtual machines and / or containers at a remote location accessible across a communication network (e.g., communication networkAttorney Docket No. : 136048-5006-WO984). One of skill in the art will appreciate that a wide array of different computer topologies is possible for the computer system 900, and other devices and systems of the preset disclosure, and that all such topologies are within the scope of the present disclosure.Moreover, rather than relying on a physical communications network 984, the illustrated devices and systems may wirelessly transmit information between each other. As such, the exemplary topology shown in Figure 10 merely serves to describe the features of some embodiments in a manner that will be readily understood to one of skill in the art.

[0171] Referring to Figure 10, in some embodiments, the computer system 900 is applied in a high-pressure steam production heat pump system. The computer system 900 is configured to control production of high-pressure steam at a heat pump system (e.g., heat pump system 104 of Figures 1-8). In some embodiments, the computer system 900 is associated with a facility (e.g., first facility 102-1 of Figure 1). In some embodiments, the computer system 900 is associated with two or more facilities 102. In some embodiments, the computer system 900 is associated with at most one facility or at most two or more facilities 102.

[0172] In some embodiments, the communication network 984 optionally includes the Internet, one or more local area networks (LANs), one or more wide area networks (WANs), other types of networks, or a combination of such networks. Examples of communication networks 984 include the World Wide Web (WWW), an intranet and / or a wireless network, such as a cellular telephone network, a wireless local area network (LAN) and / or a metropolitan area network (MAN), and other devices by wireless communication. The wireless communication optionally uses any of a plurality of communications standards, protocols and technologies, including Global System for Mobile Communications (GSM), Enhanced Data GSM Environment (EDGE), high-speed downlink packet access (HSDPA), high-speed uplink packet access (HSUPA), Evolution, Data-Only (EV-DO), HSPA, HSPA+, Dual-Cell HSPA (DC-HSPDA), long term evolution (LTE), near field communication (NFC), wideband code division multiple access (W-CDMA), code division multiple access (CDMA), time division multiple access (TDMA), Bluetooth, Wireless Fidelity (Wi-Fi) (e.g., IEEE 802. I la, IEEE 802.1 lac, IEEE 802.1 lax, IEEE 802.1 lb, IEEE 802.11g and / or IEEE 802.1 In), voice over Internet Protocol (VoIP), Wi-MAX, a protocol for e-mail (e.g., Internet message access protocol (IMAP) and / or post office protocol (POP)), instant messaging (e.g., extensible messaging and presence protocol (XMPP), Session Initiation Protocol for Instant Messaging and Presence Leveraging Extensions (SIMPLE), Instant Messaging and Presence Service (IMPS)), and / or Short Message Service (SMS), or any other suitable communicationAttorney Docket No. : 136048-5006-WO protocol, including communication protocols not yet developed as of the filing date of this document.

[0173] In various embodiments, the computer system 900 includes one or more processing units (CPUs) 972, a network or other communications interface 974, and memory 992.

[0174] In some embodiments, the computer system 900 includes a user interface 976. The user interface 976 typically includes a display 978 for presenting media, such as a status of a respective instrument (e.g., first instrument 910-1, second instrument 910-2, . . ., instrument Q 912-Q of Figure 10). In some embodiments, the display 978 is integrated within the computer systems (e.g., housed in the same chassis as the CPU 972 and memory 992). In some embodiments, the computer system 900 includes one or more input device(s) 980, which allow a subject to interact with the computer system 900. In some embodiments, input devices 980 include a keyboard, a mouse, and / or other input mechanisms. Alternatively, or in addition, in some embodiments, the display 978 includes a touch-sensitive surface (e.g., where display 978 is a touch-sensitive display or computer system 900 includes a touch pad).

[0175] In some embodiments, the computer system 900 presents media to a user through the display 978. Examples of media presented by the display 978 include one or more images, a video, audio (e.g., waveforms of an audio sample), or a combination thereof. In typical embodiments, the one or more images, the video, the audio, or the combination thereof is presented by the display 978 through a client application stored in the memory 992. In some embodiments, the audio is presented through an external device (e.g., speakers, headphones, input / output (I / O) subsystem, etc.) that receives audio information from the computer system 900 and presents audio data based on this audio information. In some embodiments, the user interface 976 also includes an audio output device, such as speakers or an audio output for connecting with speakers, earphones, or headphones.

[0176] The memory 992 includes high-speed random access memory, such as DRAM, SRAM, DDR RAM, or other random access solid state memory devices, and optionally also includes non-volatile memory, such as one or more magnetic disk storage devices, optical disk storage devices, flash memory devices, or other non-volatile solid state storage devices. The memory 992 may optionally include one or more storage devices remotely located from the CPU(s) 972. The memory 992, or alternatively the non-volatile memory device(s) within memory 992, includes a non-transitory computer readable storage medium. Access to memory 992 by other components of the computer system 900, such as the CPU(s) 972, is, optionally, controlled by a controller. In some embodiments, the memoryAttorney Docket No. : 136048-5006-WO992 can include mass storage that is remotely located with respect to the CPU(s) 972. In other words, some data stored in the memory 992 may in fact be hosted on devices that are external to the computer system 900, but that can be electronically accessed by the computer system 900 over an Internet, intranet, or other form of network 984 or electronic cable using communication interface 974.

[0177] In some embodiments, the memory 992 of the computer system 900 for producing high-pressure steam stores:• an operating system 903 (e.g. , ANDROID, iOS, DARWIN, RTXC, LINUX, UNIX, OS X, WINDOWS, or an embedded operating system such as VxWorks) that includes procedures for handling various basic system services;• optionally, an electronic address 905 associated with the computer system 900 that identifies the computer system 900 (e.g., within the communication network 984, within a network of facilities, efc.);• a control module 906 that facilitates controlling one or more operations conducted when producing high-pressure steam in accordance with a plurality of heuristic instructions, in which the control module 906 includes an instrument module 908 storing a record of a plurality of instruments 910 (e.g., first instrument 910-1, second instrument 910-2, . . ., instrument 910-Q of Figure 10) utilized for producing a high- pressure steam, and further includes a task module 912 that stores a plurality of tasks 914, each task 914 defines an operation for producing high-pressure steam at a heat pump system in accordance with one or more parameters 916 associated with a respective task 914; and• optionally, a client application 918 for presenting information e.g., media) using a display 978 of the computer system 900, such as a status of a step and / or process of a method for producing high-pressure steam.

[0178] As indicated above, an optional electronic address 905 is associated with the computer system 900. The optional electronic address 905 is utilized to at least uniquely identify the computer system 900 from other devices and components of the distributed system 900, such as other devices having access to the communication network 984 (e.g., facility 102). For instance, in some embodiments, the electronic address 905 is utilized to receive a request from a remote device associated with a first facility 102-1 to initiate producing high-pressure steam for utilization by a second facility 102-2 using the computer system 900. However, the present disclosure is not limited thereto. In some embodiments, the electronic address 905 is utilized to receive the request from the remote device associatedAttorney Docket No. : 136048-5006-WO with the first facility 102-1 to initiate producing high-pressure steam for utilization by the first facility 102-1 using the computer system 900.

[0179] In some embodiments, the computer system 900 includes a control module 906, hereinafter “controller,” that is configured to control one or more operations conducted when producing high-pressure steam. Specifically, the controller 906 is configured to control the one or more operations conducted when producing the high-pressure steam in accordance with a plurality of heuristic instructions. As a non-limiting example, in some embodiments, the plurality of heuristic instructions includes one or more proportional, integral, and derivative (PID) loop instructions and / or one or more variable frequency drive (VFD) instructions. For instance, in some embodiments, the controller 906 is in electronic communication with one or more sensors (e.g., sensor 982 of Figure 10), in which each sensor 982 in one or more sensors 982 is configured to determine a status associated with a respective instrument 910. In some embodiments, the controller 906 is in electronic communication with the one or more sensors 982 that includes a first set of sensors 982 configured to determine one or more temperatures associated with a system (e.g., a temperature of hot water received by the system 104, a temperature of low-pressure steam produced by a flash vessel structure of the system 104, a temperature of high-pressure steam produced by a compressor train of the system 104, a temperature of steam condensate source received by the system 104, a temperature of condensate produced by the system 104, a temperature loss at some or all of the system 104, efc.), a second set of sensors 982 configured to determine or more pressures associated with the system 104 (e.g., an interior pressure of the flash chamber, a pressure ratio of the compressor, a pressure loss at some or all of the system 104, etc.), a third set of sensors 982 configured to determine one or more flow rates (e.g, a mass flow rate of hot water received by the system 104, a mass flow rate of low-pressure steam produced by a flash chamber, a mass flow rate of high-pressure steam produced by a compressor, etc.) associated with the system 104, a fourth set of sensors 982 configured to determine one or more velocities associated with the system 104 (e.g, a velocity of hot water received by the system 104, a velocity of low-pressure steam produced by a flash chamber, a velocity of high-pressure steam produced by a compressor, a velocity of steam condensate source received by the system 104, etc.), a fifth set of sensors 982 configured to determine one or more electrical states associated with the system 104 (e.g., one or more electrical loads, one or more voltage drops across some or all of the system 104, one or more arc flashes, one or more groundings, etc.), or a combination thereof.Accordingly, by communicating electronically with the one or more sensors 982, theAttorney Docket No. : 136048-5006-WO controller 906 allows for the computer system 900 to control a flow rate of the high-pressure steam produced by the system 104 that is received by the facility 102. However, the present disclosure is not limited thereto.

[0180] An instrument 910 is an apparatus, device, mechanism, or a combination thereof that conducts a specific function or functions in the system 104 for producing high- pressure steam, such as for producing a high-pressure steam or a cooling water product associated with the system 104. For instance, in some embodiments, each respective instrument 910 in the plurality of instruments 910 is configured to conduct a specific task 914 or tasks 914 in the system 104 for producing high-pressure steam 140. Examples of instruments 910 include, but are not limited to, a blower, a boiler, a burner, a compressor, a conduit, a desuperheater, a drum, a heat exchanger, a fluid pump, a pipe, a reservoir, a valve, a vessel, or the like. For instance, in some embodiments, the one or more instruments 910 includes a series of at least two compressors 214 that is configured to supply the high- pressure steam 140 to an existing steam header of the facility (e.g., facility 102-1 of Figure 1). However, the present disclosure is not limited thereto.

[0181] In some embodiments, each task 914 is associated with a function, step, or process in the production of high-pressure steam 140, which is performed by a set of instruments 910. Moreover, each task 914 includes a set of parameters 916 used in the performance of a function by a respective instrument 910. In some embodiments, each task 914 is a logical dependency of operations that defines the function performed by the respective instrument 910. For instance, in some embodiments, the task 914 is a first operation to run a first instrument 910-1 with a first set of parameters 916 and a second task 914-2 is a second operation to run a second instrument 910-2. As a non-limiting example, in some embodiments, the computer system 900 configures one or more parameters 916 including configuring a flow rate parameter 916 associated with a respective instrument 910 (e.g., mass flow rate), a pressure parameter 916, a temperature parameter 916, a directional parameter 916, or the like in order to optimize production of the high-pressure steam 140 at the system 104. However, the present disclosure is not limited thereto.

[0182] Each of the above identified modules and applications correspond to a set of executable instructions for performing one or more functions described above and the methods described in the present disclosure. These modules (e.g., sets of instructions) need not be implemented as separate software programs, procedures or modules, and thus various subsets of these modules are, optionally, combined or otherwise re-arranged in various embodiments of the present disclosure. In some embodiments, the memory 992 optionallyAttorney Docket No. : 136048-5006-WO stores a subset of the modules and data structures identified above. Furthermore, in some embodiments, the memory 992 stores additional modules and data structures not described above.

[0183] It should be appreciated that the computer system 900 of Figure 10 is only one example of a computer system 900, and that the computer system 900 optionally has more or fewer components than shown, optionally combines two or more components, or optionally has a different configuration or arrangement of the components. The various components shown in Figure 10 are implemented in hardware, software, firmware, or a combination thereof, including one or more signal processing and / or application specific integrated circuits.

[0184] In some embodiments, the system 104 further includes a controller (e.g., control module 906 of Figure 10, etc.). In some embodiments, the controller 906 is configured to maintain a temperature range of the series of at least two flash chambers 204, such as maintaining a temperature of the high-pressure steam 140 that is produced by the system 104 and / or a temperature of the outlet of the system 104, such as of the cooling water source 120 associated with the facility 102.

[0185] In some embodiments, the controller receives pressure, temperature, and flow signals associated with the compressor train discharge, the facility header, and the steam recirculation manifold and generates independent actuator commands to the first valve and the second valve. In some embodiments, closed-loop regulation maintains at least one of a compressor train discharge pressure setpoint, a facility supply pressure setpoint, a recirculation manifold pressure setpoint, or a commanded recirculation flow. In some embodiments, in response to a rise in facility header pressure above a threshold, the controller throttles the first valve while commensurately opening the second valve to divert excess steam into the steam recirculation manifold and thereby stabilize compressor operating conditions. In some embodiments, upon a demand increase in the facility, the controller opens the first valve while throttling the second valve to reduce recirculation and satisfy facility load without driving the compressor train toward surge.

[0186] Accordingly, in some embodiments, the system 104 provides flexible controls to accommodates changing temperatures and flow rates without operating in an unstable condition.

[0187] Example 1: Implementations of a System for Producing High-PressureSteamAttorney Docket No. : 136048-5006-WO

[0188] Clause 1. A system for producing high-pressure steam, the system including: a compressor train including: a series of at least two compressors; an inlet of the compressor train; and an outlet of the compressor train configured to provide high-pressure steam to a facility; and a flash vessel structure including: a series of at least two flash vessels including a terminal flash vessel at one end of the flash vessel structure, wherein a vapor outlet of the terminal flash vessel is fluidly coupled to the inlet of the compressor train; vapor outlets of a remainder of the series of at least two flash vessels that are fluidly coupled between compressors of the series of at least two compressors; and a steam recirculation manifold including (i) a vapor inlet fluidly coupled to the outlet of the compressor train or an outlet of a source of high-pressure steam different from the compressor train and (ii) one or more vapor outlets, where each respective vapor outlet of the one or more vapor outlets is fluidly coupled upstream the compressor train. In some embodiments, each respective vapor outlet of the one or more vapor outlets is fluidly coupled upstream of a corresponding compressor of the compressor train.

[0189] Clause 2. The system of Clause 1, wherein the one or more vapor outlets of the steam recirculation manifold include a one-to-one relationship with the outlet of the compressor train.

[0190] Clause 3. The system of Clause 1, wherein the one or more vapor outlets of the steam recirculation manifold include a one-to-many relationship with the outlet of the compressor train.

[0191] Clause 4. The system of any preceding Clause, wherein the source of high- pressure steam is a boiler, heat recovery steam generator, or other steam generation device.

[0192] Clause 5. The system of any preceding Clause, wherein the one or more vapor outlets include a single vapor outlet.

[0193] Clause 6. The system of any preceding Clause, wherein the one or more vapor outlets include at most 20 vapor outlets.

[0194] Clause 7. The system of any preceding Clause, wherein a branch angle between a distributor channel of the steam recirculation manifold and an intermediate channel of the steam recirculation manifold is 90° or about 90°.

[0195] Clause 8. The system of any preceding Clause, wherein a branch angle between a distributor channel of the steam recirculation manifold and an intermediate channel of the steam recirculation manifold is obtuse.Attorney Docket No. : 136048-5006-WO

[0196] Clause 9. The system of any preceding Clause, wherein the steam recirculation manifold is configured to induce flow via a pressure gradient between the vapor inlet and the one or more vapor outlets of the steam recirculation manifold.

[0197] Clause 10. The system of any preceding Clause, wherein the steam recirculation manifold is configured to induce flow via a pressure gradient between the vapor inlet of the steam recirculation manifold and an inlet of another terminal flash vessel of the flash vessel structure.

[0198] Clause 11. The system of any preceding Clause, wherein a first valve selectively controls fluid communication between the outlet of the compressor train and (i) the facility and (ii) the steam recirculation manifold.

[0199] Clause 12. The system of Clause 11, wherein the first valve is configured to operate in a first position allowing at most 100 volume percent (vol%) of the high-pressure steam to flow from the outlet of the compressor train to the facility.

[0200] Clause 13. The system of either of Clauses 11 or 12, wherein the first valve is configured to operate in a second position allowing at most 100 vol% of the high-pressure steam to flow from the outlet of the compressor train to the steam recirculation manifold.

[0201] Clause 14. The system of any one of Clauses 11-13, wherein the first valve is configured to operate in a third position allowing less than 100 vol% of the high-pressure steam to flow to one of the facility and the steam recirculation manifold.

[0202] Clause 15. The system of any one of Clauses 11-14, wherein the system further includes a controller electronically coupled to the first valve and configured to modify a position of the first valve between at least two positions.

[0203] Clause 16. The system of any preceding Clause, wherein a second valve selectively controls fluid communication between a distributor channel of the steam recirculation manifold and an intermediate channel of the steam recirculation manifold.

[0204] Clause 17. The system of Clause 16, wherein the second valve is configured to operate in a first position allowing at most 100 volume percent (vol%) of the high-pressure steam to flow from the distributor channel to the intermediate channel.

[0205] Clause 18. The system of either of Clauses 16 or 17, wherein the second valve is configured to operate in a second position allowing at most 100 vol% of the high-pressure steam to flow from the distributor channel to the intermediate channel.

[0206] Clause 19. The system of any one of Clauses 16-18, wherein the second valve is configured to operate in a third position allowing less than 100 vol% of the high-pressure steam to flow from the distributor channel to the intermediate channel.Attorney Docket No. : 136048-5006-WO

[0207] Clause 20. The system of any one of Clauses 16-19, wherein the system further includes a controller electronically coupled to the second valve and configured to modify a position of the second valve between at least two positions.

[0208] Clause 21. The system of any one of Clauses 16-20, wherein a pitch of the distributor channel is 0° or substantially 0°.

[0209] Clause 22. The system of any one of Clauses 16-21, wherein a pitch of the intermediate channel is 0° or substantially 0°.

[0210] Clause 23. The system of any preceding Clause, wherein the system further includes: a first sensor configured to detect a pressure associated with the compressor train, and the controller that is electrically coupled to the first sensor and the first valve, and / or is further configured to maintain the pressure of the compressor train.

[0211] Clause 24. The system of any preceding Clause, wherein the system further includes: a second sensor configured to detect a pressure associated with the flash vessel structure, and the controller that is electrically coupled to the second sensor and a second valve, and is further configured to maintain the pressure of the flash vessel structure.

[0212] Clause 25. The system of any preceding Clause, wherein the system further includes: a third sensor configured to detect a pressure associated with the steam recirculation manifold, and the controller that is electrically coupled to the third sensor and both (i) the first valve and (ii) a second valve and is further configured to maintain the pressure of the steam recirculation manifold.

[0213] Clause 26. The system of any preceding Clause, wherein the system further includes: a fourth sensor configured to detect a flow rate associated with the compressor train, and the controller that is electrically coupled to the fourth sensor and a first valve and / or a second valve, and is further configured to maintain the flow rate of the compressor train.

[0214] Clause 27. The system of any preceding Clause, wherein the system further includes: a fifth sensor configured to detect a flow rate associated with the flash vessel structure, and the controller that is electrically coupled to the fifth sensor and a second valve, and is further configured to maintain the flow rate of the flash vessel structure.

[0215] Clause 28. The system of any preceding Clause, wherein the system further includes: a sixth sensor configured to detect a flow rate associated with the steam recirculation manifold, and the controller that is electrically coupled to the sixth sensor and both (i) a first valve and (ii) a second valve and is further configured to maintain the flow rate of the steam recirculation manifold.Attorney Docket No. : 136048-5006-WO

[0216] Clause 29. The system of any preceding Clause, wherein the system further includes: a seventh sensor configured to detect a resource consumption associated with the compressor train, and the controller that is electrically coupled to the seventh sensor and the first valve and / or a second valve is further configured to maintain the resource consumption of the compressor train.

[0217] Clause 30. The system of any preceding Clause, wherein the system further includes: an eighth sensor configured to detect a resource consumption associated with the flash vessel structure, and the controller that is electrically coupled to the eighth sensor and a second valve, and is further configured to maintain the resource consumption of the flash vessel structure.

[0218] Clause 31. The system of any preceding Clause, wherein the system further includes: a ninth sensor configured to detect a resource consumption rate associated with the steam recirculation manifold, and the controller that is electrically coupled to the ninth sensor and both (i) a first valve and (ii) a second valve and is further configured to maintain the resource consumption of the steam recirculation manifold.

[0219] Clause 32. The system of any preceding Clause, wherein the system further includes a drain manifold configured to receive liquid condensate of the steam recirculation manifold.

[0220] Clause 33. The system of Clause 32, wherein the drain manifold includes at least one channel fluidly coupled between a reservoir of the drain manifold and one of a distributor channel and an intermediate channel.

[0221] Clause 34. The system of Clause 33, wherein the at least one channel of the drain manifold includes a one-to-many relationship with the intermediate channel.

[0222] Clause 35. The system of Clause 33, wherein the at least one channel of the drain manifold includes a single channel.

[0223] Clause 36. The system of Clause 33, wherein the at least one channel of the drain manifold includes at most 20 channels.

[0224] Clause 37. The system of any preceding Clause, wherein each respective vapor outlet of the one or more vapor outlets is fluidly coupled to a vapor inlet of a corresponding flash vessel in the flash vessel structure.

[0225] Example 2: A steam recirculation manifold for Producing High Pressure SteamAttorney Docket No. : 136048-5006-WO

[0226] A system included a steam recirculation manifold. A steam header traversed the length of the system in a pipe rack. A discharge of a terminal compressor was connected to the steam header. One or more branches from the header brought steam back to a suction side of a flash vessel structure, preferably to each flash vessel of the flash vessel structure, but at least one flash vessel received a branch from the steam header.

[0227] The steam recirculation manifold had multiple purposes. First, the steam recirculation manifold served as a source of steam when the system was offline. When the system was tied to an existing steam system, live steam was brought through the steam recirculation header to feed the flash vessel structure. This was useful for air purging during the startup sequence and was utilized for feeding steam to shaft seals, if present, to keep air from being pulled into stages that operated at vacuum pressures. Steam was used to preheat the system to avoid some level of condensation caused by cold metal surfaces during startup. The steam was used to deaerate the liquid loop by circulating water through the loop while steam was fed to the system. Air trapped in the water gradually came out of solution as the temperature increased.

[0228] Second, the recirculation steam system enabled the system to run in a closed- loop operating point, where the main valve on the steam discharge was closed, and all steam discharged by the system was recirculated back into its suction. This enabled the system to operate anywhere from extremely low power to full power while remaining isolated from the facility steam system. This was useful for commissioning, startup and shutdown, and entering a low power mode where the system was still running at greatly reduced speeds, which enabled a fast restart. Another operating mode was where the main steam isolation valve was left open, but a portion of steam was recirculated. This allowed the system to trim its net steam production to very low flows while remaining fully operational. If such a system was not in place, when steam demand became low, the system only turned down to some limit before having to turn off. By recirculating steam, however, the turndown capability was greatly increased.

[0229] Third, the recirculation steam system provided steam for the anti-surge control (ASC) system. In the event that a compressor was operating at too low of a flow rate for its given speed, surge occurred, which negatively affected system performance and caused catastrophic mechanical failure to the fan components. To avoid surge, a valve on the branch from the header opened to allow high-pressure steam to flow through the branch and into the suction connection of the flash vessel structure. This increased the steam flow rate through the flash vessel and moved the operation away from surge. The control valve responded to aAttorney Docket No. : 136048-5006-WO number of signals that identified surge or approaching surge such as pressure gradients, measured or calculated flow rates, and fan power usage.

[0230] Finally, the recirculation steam manifold was used to make certain fan trains work that did not work without it. The recirculation steam manifold was used to send steam to fans that had too low volume flow to avoid surge conditions. Flash vessel structures were generally used for large systems that moved a lot of steam. Some deployments called for smaller amounts of steam. If this small mass flow system was also required to produce high- pressure steam, it was difficult to find a flash vessel small enough to handle this very small volume flow of steam. If steam volume flow was too low, the fan surged, recirculation steam manifold took steam off the discharge of the fan train and sent it to the inlet of any fans that would otherwise surge. Rather than responding to occasional surge, recirculation of steam was built into the design so that it typically ran with some amount of recirculation.

[0231] The steam recirculation header was either separate from the steam supply header that connected the system to the facility or was shared. In the separate configuration, the steam recirculation header teed into the main steam supply header and pulled steam back to the compressor train. In the shared configuration, the compressor train discharged into the shared steam recirculation header and main steam supply header. Branches were pulled from that line to feed the flash vessel structure, and at the end of the line was the main isolation valve that separated the compressor train from the facility steam system.

[0232] Regardless of configuration or operational case, condensation formed inside the steam recirculation manifold. Typically, channels were pitched for gravity-assisted liquid drainage. Due to the horizontal construction of the channels, the channels had no pitch. To manage the condensate, the steam recirculation header was located vertically above one or more condensate drain headers in the pipe rack. Periodically along the length of the pipe rack, preferably once per modular pipe skid, a drip leg connected from the steam recirculation header to the condensate drain header. The drip leg captured condensed liquid in the piping and sent it to the condensate drain system. In this drip leg, a steam trap, orifice, needle valve, or other method of controlling flow was utilized to allow the correct amount of liquid to move through without carrying much or any live steam into the condensate drain header.

[0233] All references cited herein are incorporated herein by reference in their entirety and for all purposes to the same extent as if each individual publication or patent or patent application is specifically and individually indicated to be incorporated by reference in its entirety for all purposes.Attorney Docket No. : 136048-5006-WO

[0234] Many modifications and variations of this invention can be made without departing from its spirit and scope, as will be apparent to those skilled in the art. The specific embodiments described herein are offered by way of example only. The embodiments are chosen and described in order to best explain the principles of the invention and its practical applications, to thereby enable others skilled in the art to best utilize the invention and various embodiments with various modifications as are suited to the particular use contemplated. The invention is to be limited only by the terms of the appended claims, along with the full scope of equivalents to which such claims are entitled.

Claims

Attorney Docket No. : 136048-5006-WOWhat is claimed is:

1. A system for producing high-pressure steam, the system comprising: a compressor train comprising: a series of at least two compressors; an inlet of the compressor train; and an outlet of the compressor train configured to provide high-pressure steam to a facility; and a flash vessel structure comprising: a series of at least two flash vessels comprising a terminal flash vessel at one end of the flash vessel structure, wherein a vapor outlet of the terminal flash vessel is fluidly coupled to the inlet of the compressor train; vapor outlets of a remainder of the series of at least two flash vessels that are fluidly coupled between compressors of the series of at least two compressors; and a steam recirculation manifold comprising (i) a vapor inlet fluidly coupled to the outlet of the compressor train or an outlet of a source of high-pressure steam different from the compressor train and (ii) one or more vapor outlets, wherein each respective vapor outlet of the one or more vapor outlets is fluidly coupled upstream of a corresponding compressor of the compressor train.

2. The system of claim 1, wherein the one or more vapor outlets of the steam recirculation manifold comprise a one-to-one relationship with the outlet of the compressor train.

3. The system of claim 1, wherein the one or more vapor outlets of the steam recirculation manifold comprise a one-to-many relationship with the outlet of the compressor train.

4. The system of any preceding claim, wherein the source of high-pressure steam is a boiler, a heat recovery steam generator, or other steam generation device.

5. The system of any preceding claim, wherein the one or more vapor outlets comprises a single vapor outlet.

6. The system of any preceding claim, wherein the one or more vapor outlets comprises at most 20 vapor outlets.Attorney Docket No. : 136048-5006-WO7. The system of any preceding claim, wherein a branch angle between a distributor channel of the steam recirculation manifold and an intermediate channel of the steam recirculation manifold is 90° or about 90°.

8. The system of any preceding claim, wherein a branch angle between a distributor channel of the steam recirculation manifold and an intermediate channel of the steam recirculation manifold is obtuse.

9. The system of any preceding claim, wherein the steam recirculation manifold is configured to induce flow via a pressure gradient between the vapor inlet and the one or more vapor outlets of the steam recirculation manifold.

10. The system of any preceding claim, wherein the steam recirculation manifold is configured to induce flow via a pressure gradient between the vapor inlet of the steam recirculation manifold and an inlet of another terminal flash vessel of the flash vessel structure.

11. The system of any preceding claim, wherein a first valve selectively controls fluid communication between the outlet of the compressor train and (i) the facility (ii) and the steam recirculation manifold.

12. The system of claim 11, wherein the first valve is configured to operate in a first position allowing at most 100 volume percent (vol%) of the high-pressure steam to flow from the outlet of the compressor train to the facility.

13. The system of claim 11 or 12, wherein the first valve is configured to operate in a second position allowing at most 100 vol% of the high-pressure steam to flow from the outlet of the compressor train to the steam recirculation manifold.

14. The system of any one of claims 11-13, wherein the first valve is configured to operate in a third position allowing less than 100 vol% of the high-pressure steam to flow to one of the facility and the steam recirculation manifold.

15. The system of any one of claims 11-14, where the system further comprises a controller electronically coupled to the first valve and configured to modify a position of the first valve between at least two positions.Attorney Docket No. : 136048-5006-WO16. The system of any preceding claim, wherein a second valve selectively controls fluid communication between a distributor channel of the steam recirculation manifold and an intermediate channel of the steam recirculation manifold.

17. The system of claim 16, wherein the second valve is configured to operate in a first position allowing at most 100 volume percent (vol%) of the high-pressure steam to flow from the distributor channel to the intermediate channel.

18. The system of claim 16 or 17, wherein the second valve is configured to operate in a second position allowing at most 100 vol% of the high-pressure steam to flow from the distributor channel to the intermediate channel.

19. The system of any one of claims 16-18, wherein the second valve is configured to operate in a third position allowing less than 100 vol% of the high-pressure steam to flow from the distributor channel to the intermediate channel.

20. The system of any one of claims 16-19, where the system further comprises a controller electronically coupled to the second valve and configured to modify a position of the second valve between at least two positions.

21. The system of any one of claims 16-20, wherein a pitch of the distributor channel is 0° or substantially 0°.

22. The system of any one of claims 16-21, wherein a pitch of the intermediate channel is 0° or substantially 0°.

23. The system of any preceding claim, wherein the system further comprises: a first sensor configured to detect a pressure associated with the compressor train, and the controller that is electrically coupled to the first sensor and the first valve, and / or is further configured to maintain the pressure of the compressor train.

24. The system of any preceding claim, wherein the system further comprises: a second sensor configured to detect a pressure associated with the flash vessel structure, and the controller that is electrically coupled to the second sensor and a second valve, and is further configured to maintain the pressure of the flash vessel structure.

25. The system of any preceding claim, wherein the system further comprises:Attorney Docket No. : 136048-5006-WO a third sensor configured to detect a pressure associated with the steam recirculation manifold, and the controller that is electrically coupled to the third sensor and both (i) the first valve and (ii) a second valve and is further configured to maintain the pressure of the steam recirculation manifold.

26. The system of any preceding claim, wherein the system further comprises: a fourth sensor configured to detect a flow rate associated with the compressor train, and the controller that is electrically coupled to the fourth sensor and a first valve and / or a second valve, and is further configured to maintain the flow rate of the compressor train.

27. The system of any preceding claim, wherein the system further comprises: a fifth sensor configured to detect a flow rate associated with the flash vessel structure, and the controller that is electrically coupled to the fifth sensor and a second valve, and is further configured to maintain the flow rate of the flash vessel structure.

28. The system of any preceding claim, wherein the system further comprises: a sixth sensor configured to detect a flow rate associated with the steam recirculation manifold, and the controller that is electrically coupled to the sixth sensor and both (i) a first valve and (ii) a second valve and is further configured to maintain the flow rate of the steam recirculation manifold.

29. The system of any preceding claim, wherein the system further comprises: a seventh sensor configured to detect a resource consumption associated with the compressor train, and the controller that is electrically coupled to the seventh sensor and the first valve and / or a second valve is further configured to maintain the resource consumption of the compressor train.

30. The system of any preceding claim, wherein the system further comprises: a eighth sensor configured to detect a resource consumption associated with the flash vessel structure, andAttorney Docket No. : 136048-5006-WO the controller that is electrically coupled to the eighth sensor and a second valve, and is further configured to maintain the resource consumption of the flash vessel structure.

31. The system of any preceding claim, wherein the system further comprises: a ninth sensor configured to detect a resource consumption rate associated with the steam recirculation manifold, and the controller that is electrically coupled to the ninth sensor and both (i) a first valve and (ii) a second valve and is further configured to maintain the resource consumption of the steam recirculation manifold.

32. The system of any preceding claim, wherein the system further comprises a drain manifold configured to receive liquid condensate of the steam recirculation manifold.

33. The system of claim 32, wherein the drain manifold comprises at least one channel fluidly coupled between a reservoir of the drain manifold and one of a distributor channel and an intermediate channel.

34. The system of claim 33, wherein the at least one channel of the drain manifold comprises a one-to-many relationship with the intermediate channel.

35. The system of claim 33, wherein the at least one channel of the drain manifold comprises a single channel.

36. The system of claim 33, wherein the at least one channel of the drain manifold comprises at most 20 channels.

37. The system of any preceding claim, wherein each respective vapor outlet of the one or more vapor outlets is fluidly coupled to a vapor inlet of a corresponding flash vessel in the flash vessel structure.

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