Systems, methods and apparatus for generating high-pressure steam

Abstract

A system, method, and apparatus for generating high-pressure steam are provided. The compressor train includes a series of at least two compressors, a compressor train inlet, and a compressor train outlet. The compressor train outlet is configured to supply high-pressure steam to a facility. The flash vessel train includes a series of at least two flash vessels. The series of at least two flash vessels includes an end flash vessel located at one end of the flash vessel train. Further, a vapor outlet of the end flash vessel is fluidly coupled to the inlet of the compressor train. Further, vapor outlets of the remaining flash vessels in the series are fluidly coupled between the at least two compressors in the series.

Description

[Technical Field]

[0001] (CROSS-REFERENCE TO RELATED APPLICATIONS) This application claims priority to U.S. Provisional Patent Application No. 63 / 371,837, filed August 18, 2022, entitled "Steam Generating Mechanical Vapor Recompression Heat Pump," the entire contents of which are incorporated herein by reference for all purposes.

[0002] FIELD OF THE DISCLOSURE The present disclosure relates generally to systems, methods and apparatus for generating high pressure steam. [Background technology]

[0003] On-site emissions reductions in industries are crucial to achieving desired greenhouse gas targets. For example, the California Air Resources Board's AB32 and SB32 greenhouse gas reduction targets prescribe a set of greenhouse gas targets, but the specific set of greenhouse gas targets should not be considered the only goals that industries must achieve. Currently, industrial manufacturing plants burn natural gas in steam boilers to evaporate water and produce steam. When the thermal energy of the steam is put to beneficial use, it is removed from the process through a cooling water loop, which increases the temperature of the cooling water. The warmed cooling water is then typically sent to a cooling tower, where the thermal energy is released to the atmosphere, i.e., wasted, to reduce the temperature of the cooling water.

[0004] To meet greenhouse gas targets and achieve carbon neutrality, it is desirable to expand industrial electrification. Industrial electrification includes the electrification of gas-fired boilers in various industries. For example, industrial sectors that have been particularly highlighted for improvement include the chemical sector, which uses natural gas boilers for steam generation, the pulp and paper sector, food production-related sectors, and a variety of other industrial sectors. These and other sectors are believed to be able to move closer to achieving energy targets.

[0005] Achieving desired energy targets is hindered by the lack of efficient and economical technologies to electrify the large-scale thermal energy demands associated with steam generation in industries, including those mentioned above. Currently, state-of-the-art industrial heat pumps cannot reach the temperatures necessary to generate the medium- and high-pressure saturated steam required for many industrial facilities. Meanwhile, state-of-the-art electric boiler technology can indeed reach the required temperatures and pressures, but has a low coefficient of performance (COP) of less than 1.0. This results in excessive power consumption, making these systems uneconomical to operate. Furthermore, high power consumption can place an excessive strain on the power grid.

[0006] It is also desirable that the development of alternative electric boiler technologies to meet medium- and high-pressure saturated steam demands be accomplished in a manner that limits custom engineering and specialized, one-off field assembly. This custom engineering and specialized, one-off field assembly significantly limits availability and increases costs, which is believed to affect industrial customers' perceptions of reliability. Furthermore, customized solutions with specialized field assembly can generally result in very expensive downtime. This makes industrial customers reluctant to try new technologies that may fail and / or cause unwanted downtime.

[0007] Currently available state-of-the-art heat pumps typically use hydrofluorocarbon (HFC) or hydrofluoroolefin (HFO) refrigerants to generate thermal energy at temperatures up to 320°F. These known systems cannot generate steam directly and must be used in conjunction with a non-combustion steam generator, reducing the nominal temperature by 20°F. As a result, the maximum saturated vapor pressure these systems can generate is 3.5 barg (50 psig), which is not high enough to support the medium-pressure (3.5-20 barg) applications commonly found in manufacturing. Furthermore, these systems have a relatively low coefficient of performance (coefficient of performance) of less than 3.0, resulting in high power demands and high operating costs. HFC refrigerants have a high global warming potential, while HFO refrigerants have a low global warming potential but are expensive.

[0008] CO2-based heat pumps also utilize a low-cost, low-global-warming-potential refrigerant (CO2), but the required high pressure of the refrigerant limits its temperature to approximately 238°F or less. Although 238°F is above the boiling point of water at atmospheric pressure, CO2-based heat pumps cannot generate steam. This is because CO2-based heat pumps require a low reflux temperature of 203°F or less, and the driving capacity of the steam generator is generally determined by this reflux temperature.

[0009] Ammonia-based heat pumps employ more mature technology, but, like CO2-based heat pumps, are not suitable for steam generation because the high-pressure characteristics of the system limit its maximum output temperature to approximately 203°F. Ammonia-based systems are capable of generating lower temperatures, making them complementary, not competitive, to steam-generating heat pump systems. For example, ammonia-based systems are commonly used in the food manufacturing industry to achieve low-temperature refrigeration, typically emitting waste heat at temperatures ranging from approximately 85°F to 100°F.

[0010] There is a need for an improved arrangement that overcomes at least one or more of the above-mentioned shortcomings and provides additional features and advantages in a cost-effective, efficient, reliable, scalable, etc. manner.

[0011] In light of the above background, there is a need in the art for systems, methods, and apparatus for electrifying the production of high-pressure steam. Various implementations of the present application are efficient in energy consumption and manufacturing costs.

[0012] Accordingly, various aspects of the present disclosure are directed to systems, methods, and apparatus for generating high-pressure steam. For example, in some embodiments, the disclosed systems, methods, and apparatus are configured as heat pumps. In some embodiments, the disclosed heat pumps are configured as open-cycle mechanical vapor recompression and high-pressure steam generation heat pumps. In some embodiments, the disclosed systems, methods, and apparatus are configured to replace conventional fossil fuel (e.g., natural gas) boilers and / or conventional evaporative cooling towers, thereby reducing overall energy consumption and conserving water. More specifically, in some embodiments, the disclosed systems, methods, and apparatus provide highly efficient high-pressure heat pumps that receive hot water, such as cooling water, from a facility and provide high-pressure steam by supplying it to a flash vessel train, the pressure of which is maintained below the saturation pressure of the hot water to simultaneously cool the hot water and generate steam (e.g., low-pressure steam). The flash vessel train is configured to supply the low-pressure steam to a compressor train, which is configured to compress the low-pressure steam generated in the flash vessel to generate high-pressure steam at a desired facility pressure. Thus, in some embodiments, the disclosed systems, methods, and apparatus produce high-pressure steam at temperatures up to 426 degrees Fahrenheit (219 degrees Celsius (°C)), with pressures up to 315 pounds per square inch gauge (PSI) (19.0 Barg) and temperature rises up to 330°F (166°C). Summary of the Invention

[0013] Additionally, in some embodiments, the disclosed systems, methods, and apparatus provide a modularly configurable reference heat pump system based on interchangeable subassemblies of the compressor train and / or flash vessel train of the heat pump system. Thus, in some embodiments, the disclosed systems, methods, and apparatus provide a stand-alone heat pump that is not deeply integrated into the processes associated with a facility. Rather, the disclosed systems, methods, and apparatus connect to the facility with standard components, including a hot water source and a steam header, but otherwise operate outside of the processes associated with the facility.

[0014] More specifically, one aspect of the present disclosure is directed to providing a system for generating high-pressure steam. The system includes a compressor train. The compressor train includes a series of at least two compressors. The compressor train also includes a compressor train inlet. The compressor train further includes a compressor train outlet configured to supply high-pressure steam to a facility. The system further includes a flash vessel train. The flash vessel train includes a series of at least two flash vessels, the series of at least two flash vessels further including an end flash vessel located at one end of the flash vessel train. The vapor outlet of the end flash vessel is fluidly coupled to the inlet of the compressor train. The system also includes a vapor outlet of the remaining series of at least two flash vessels fluidly coupled between the series of at least two compressors.

[0015] In some embodiments, the flash vessel train further includes a flash vessel train inlet configured to receive hot water from the facility or another facility.

[0016] In some embodiments, each of the remainder of the series of at least two flash vessels includes a liquid outlet fluidly coupled to an inlet of another flash vessel in the series of at least two flash vessels.

[0017] In some embodiments, the end-flush vessel includes a liquid outlet fluidly coupled to the outlet of the system.

[0018] In some embodiments, the system further includes a controller configured to maintain a temperature range of the flash vessel train between the temperature of the high-pressure steam and the temperature at the outlet of the system.

[0019] In some embodiments, the series of at least two compressors includes centrifugal compressors. In some embodiments, the controller is configured to prevent stalling or surging in the centrifugal compressors.

[0020] In some embodiments, the end-flush vessel includes a liquid outlet fluidly coupled to a re-pressurization pump, which is connected to the outlet of the system.

[0021] In some embodiments, each of the series of at least two flash vessels is configured to maintain an internal pressure below the saturation pressure of the hot water input to each of the flash vessels, and each of the series of at least two flash vessels is configured to expand the hot water to produce low-pressure steam.

[0022] In some embodiments, the end-of-life flush vessel further includes an inlet configured to receive heated water, which may be received from the facility or another facility.

[0023] In some embodiments, the end-of-life flush vessel further includes an inlet configured to receive hot water from the facility or another facility, and the end-of-life flush vessel further includes a liquid outlet fluidly coupled to a repressurization pump, which is further connected to an outlet of the system, which is further fluidly coupled to a heat exchange mechanism associated with the hot water received from the facility or another facility.

[0024] In some embodiments, the system further includes an attemperator train including at least one attemperator, each attemperator in the attemperator train including an outlet configured to inject hot water received from the facility or another facility into the compressor train.

[0025] In some embodiments, at least one attemperator of the attemperator train is configured to control the flow rate of fluid through the attemperator.

[0026] In some embodiments, the controller is configured to modify the flow rate of fluid through the attemperator in accordance with a determination that the temperature and / or pressure associated with the compressor train meets a first pressure and / or a first temperature.

[0027] In some embodiments, the system has a coefficient of performance greater than 65% of the corresponding Carnot efficiency.

[0028] In some embodiments, a flash vessel in the flash vessel train includes a continuous blowdown configured to remove contaminants contained in the flash vessel.

[0029] In some embodiments, the system further includes a boiler interposed between an output of the terminal compressor of the compressor train and an outlet of the compressor train and fluidly coupled to the output and the outlet.

[0030] In some embodiments, the system further includes a vapor accumulator interposed between an output of the terminal compressor of the compressor train and an outlet of the compressor train, and fluidly coupled to the output and the outlet.

[0031] In some embodiments, the compressor train includes between 2 and 20 compressors, inclusive.

[0032] In some embodiments, the compressor train includes m compressors, where m is an integer greater than 2, and m is selected depending on the temperature of the high pressure steam and the temperature of the hot water received from the facility or another facility.

[0033] In some embodiments, there is a one-to-one relationship between each compressor in the compressor train and each flash vessel in the flash vessel train.

[0034] In some embodiments, the compressor train includes a first compressor and a second compressor, the first compressor having a first size and the second compressor having a second size smaller than the first size, and the first compressor is coupled upstream of the second compressor in the compressor train.

[0035] In some embodiments, the compressor train includes a third compressor interposed between and fluidly coupled to the first compressor and the second compressor, the third compressor including either the first size or the second size.

[0036] In some embodiments, each compressor in the compressor train has a compression ratio of less than 2.5.

[0037] In some embodiments, the compressor train outlet is configured to provide high pressure steam at a pressure between 50 pounds per square inch gauge (PSIg) (3.4 Barg) and 315 PSIg (21.7 Barg), inclusive.

[0038] In some embodiments, the controller is configured to maintain pressure at the outlet of the compressor train by varying the rotational speed of each compressor in the compressor train.

[0039] In some embodiments, a flash vessel in the flash vessel train includes a second liquid outlet configured to be fluidly connected to selectively remove fluid from the corresponding flash vessel.

[0040] In some embodiments, the system further includes a controller in electrical communication with the second liquid outlet. In some such embodiments, the controller is configured to control the selective removal of fluid from the flash vessel.

[0041] In some embodiments, the controller is configured to modify the flow rate of fluid through the attemperator in accordance with a determination that the temperature and / or pressure associated with the compressor train meets a first pressure and / or a first temperature.

[0042] In some embodiments, the series of at least two compressors includes at least four compressors. In some such embodiments, the at least four compressors are arranged to form a herringbone arrangement.

[0043] In some embodiments, the system further includes a water loop. In some embodiments, the water loop includes an upstream portion and a downstream portion. In some embodiments, the downstream portion is configured to receive heated water from the same or another facility. In some embodiments, the upstream portion is configured to supply chilled water to the same or another facility. Also, in some embodiments, the water loop is heated by the same or another facility.

[0044] The systems, methods, and apparatus of the present disclosure have other features and advantages that will become apparent from, or are further described in detail in, the accompanying drawings and the following detailed description, which together serve to explain certain principles of the invention. [Brief explanation of the drawings]

[0045] [Figure 1A] FIG. 1 is a block diagram of an exemplary high-pressure steam generation heat pump system, where dashed boxes represent optional elements, according to some embodiments.

[0046] [Figure 1B]FIG. 1 is a block diagram of an exemplary high-pressure steam generation heat pump system, where dashed boxes represent optional elements, according to some embodiments.

[0047] [Figures 2A, 2B, 3, 4, 5A, 5B, and 5C] FIG. 1 is a block diagram of an exemplary high-pressure steam generation heat pump system, where dashed boxes represent optional elements, according to some embodiments.

[0048] [Figure 6] 1 is a chart illustrating various parameters associated with various high pressure steam generating heat pump systems, according to some embodiments.

[0049] [Figure 7] FIG. 1 is a chart comparing the performance of a high-pressure steam generation heat pump system according to some embodiments with various prior art technologies.

[0050] [Figure 8] 1 is a flowchart of an exemplary method for generating high-pressure steam, according to some embodiments, where dashed boxes represent optional elements in the flowchart.

[0051] [Figure 9] FIG. 1 is a block diagram illustrating an exemplary computer system applied to a high-pressure steam generating heat pump system, according to some embodiments.

[0052] In the drawings, reference numerals refer to the same or corresponding parts of the invention throughout the several views of the drawings. DETAILED DESCRIPTION OF THE INVENTION

[0053] The present disclosure provides a system, method, and apparatus for generating high-pressure steam. The compressor train includes a series of at least two compressors, a compressor train inlet, and a compressor train outlet. In some embodiments, each compressor in the compressor train is a centrifugal compressor. The compressor train outlet is configured to supply high-pressure steam to a facility, thereby coupling the compressor train to the facility. In some embodiments, the compressor train is coupled (e.g., directly connected) to the facility. The flash vessel train includes a series of at least two flash vessels. The series of at least two flash vessels includes an end flash vessel located at one end of the flash vessel train. In some embodiments, the flash vessel train is configured to convert heat associated with hot water received in the system into latent heat. Further, a vapor outlet of the end flash vessel is fluidly coupled to the inlet of the compressor train. The system further includes a vapor outlet of the remainder of the series of at least two flash vessels fluidly coupled between the series of at least two compressors. Thus, each flash vessel in the flash vessel train generates low pressure steam and supplies it to each compressor in the compressor train to increase the pressure of the low pressure steam, e.g., to generate high pressure steam.

[0054] Reference will now be made in detail to the 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 those skilled 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.

[0055] In this specification, terms such as "first," "second," etc. may be used to describe various elements, but it should be understood that these elements are not limited by these terms. These terms are used merely to distinguish one element from another. For example, a first compressor may be referred to as a second compressor, and similarly, a second compressor may be referred to as a first compressor, without departing from the scope of this disclosure. Both the first compressor and the second compressor are compressors, but they are not the same compressor.

[0056] The terminology used in this 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 dictates otherwise. As used herein, the term "and / or" should also be understood to refer to and encompass any and all possible combinations of one or more of the associated listed items. As used herein, it should be further understood that the terms "comprises" and / or "comprising" specify the presence of stated features, integers, steps, operations, elements, and / or components, but do not exclude the presence or addition of one or more other features, integers, steps, operations, elements, components, and / or groups thereof.

[0057] The foregoing description has included example systems, methods, techniques, instruction sequences, and computer program products embodying example 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. However, it will be apparent to those skilled in the art that implementations of the inventive subject matter may be practiced without these specific details. Generally, well-known instruction instances, protocols, structures, and techniques have not been shown in detail.

[0058] The foregoing description has been set forth with reference to specific implementations for purposes of explanation. However, the exemplary description below is not intended to be exhaustive or to limit the implementations to the precise forms disclosed. Many modifications and variations are possible in light of the above teachings. The implementations have been chosen and described to best explain the principles and their practical applications, and to enable others skilled in the art to best utilize the implementations and various implementations with various modifications suited to the particular applications contemplated.

[0059] For clarity, not all of the routine features of the implementations described herein are shown and described. It is to be understood that in developing any such actual implementation, numerous implementation-specific decisions will be made to achieve the designer's particular goals, such as adherence to use cases and business-related constraints, and that these particular goals will vary from implementation to implementation and from designer to designer. It is also to be understood that such a design effort may be complex and time-consuming, but would nevertheless be a routine undertaking of engineering for one of ordinary skill in the art having the benefit of this disclosure.

[0060] As used herein, the term "if" may be interpreted to mean "when," or "upon," or "in response to determining," or "in response to detecting," depending on the context. Similarly, the phrases "if it is determined," or "if [the stated condition or event] is detected," may be interpreted 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.

[0061] As used herein, the terms "about" or "approximately" can mean within an acceptable error range for a particular value as determined by one of ordinary skill in the art, which may depend in part on how the value is measured or determined, e.g., the limitations of the measurement system. For example, "about" may mean within one standard deviation or more than one standard deviation, in accordance with practice in the art. "About" may mean within a range of ±20%, ±10%, ±5%, or ±1% of a given value. When a particular value is described in this application and claims, unless otherwise specified, the term "about" means within an acceptable error range for the particular value. The term "about" may have the meaning commonly understood by one of ordinary skill in the art. The term "about" may refer to ±10%. The term "about" may refer to ±5%.

[0062] As used herein, the term "epoch" means a predetermined period of time.

[0063] Furthermore, in this specification, the terms "compressor" and "blower" are used interchangeably unless expressly stated otherwise.

[0064] In this specification, the terms "flash vessel" and "knockout drum" are used interchangeably unless expressly stated otherwise.

[0065] In this specification, the terms "steam" and "water vapor" are used interchangeably unless expressly stated otherwise.

[0066] Also, as used herein, the term "stream" refers to any material moving or en route, directly or indirectly, from one location to another. In some embodiments, a stream remains a stream even if it is temporarily stationary at any epoch. It should be understood that in some embodiments, when a particular stream is referred to in this disclosure, this does not necessarily refer to a single pipe or other physical conveying means.

[0067] Furthermore, when a reference number is indicated by the notation "ith," it refers to a generic component, set, or embodiment. For example, a compressor referred to as "compressor i" refers to the i-th compressor of the plurality of compressors (e.g., compressor 204-i of the plurality of compressors 204).

[0068] 1A and 1B each depict a block diagram of an exemplary high-pressure steam generation heat pump system according to some embodiments, with dashed boxes representing optional elements. Figures 2A-5C depict block diagrams of illustrative high-pressure steam generation heat pump systems according to some embodiments, with dashed boxes representing optional elements. With reference to FIGS. 1A and 1B, in some embodiments, the present disclosure is directed to providing a system (e.g., system 104 of any of FIGS. 1A-7) for generating high-pressure steam (e.g., high-pressure steam 140-1 or 140-2 of FIG. 1A, high-pressure steam 140 of FIG. 1B, high-pressure steam 140 of any of FIGS. 2A-7, etc.).

[0069] In some embodiments, the system 104 is coupled to one or more facilities (e.g., the first facility 102-1 in FIG. 1A , the second facility 102 in FIG. 1B , etc.). For example, in some embodiments, the system 104 is associated with and located near the first facility 102-1, thereby utilizing one or more resources from the first facility 102-1. Also, in some embodiments, the system 104 is associated with and located near the first facility 102-1, for example, by coupling to an existing steam header of the first facility 102-1, so that the system 104 can provide high-pressure steam 140 to the first facility 102-1. However, the present disclosure is not limited in this respect.

[0070] 2A-5C, system 104 includes a compressor train (e.g., compressor train 202 in any of FIGS. 2A-5C) and a flash vessel train (e.g., flash vessel 212 in any of FIGS. 1A-5B), both of which are used in conjunction by system 104 to generate high-pressure steam 140 for facility 102.

[0071] Those skilled in the art will appreciate that temperature rise and mechanical stresses within each compressor limit the maximum pressure differential that can be provided across any stage of each compressor. Accordingly, to provide high-pressure steam 140 available to facility 102, compressor train 202 includes a series of at least two compressors (e.g., first compressor 204-1 in any of FIGS. 2A-5C, second compressor 204-2 in any of FIGS. 2A-5C, third compressor 204-3 in any of FIGS. 3-5C, ..., compressor 204-m in FIG. 5C, etc.). For example, in some embodiments, the compressor train 202 may include between 2 and 20 compressors 204 (e.g., 2 compressors 204, 3 compressors 204, ..., 20 compressors 204, etc.), between 2 and 17 compressors 204, between 2 and 15 compressors 204, between 2 and 12 compressors 204, between 2 and 9 compressors 204, between 2 and 6 compressors 204, between 2 and 3 compressors 204, between 3 and 20 compressors 204, between 3 and 17 compressors 204, between 3 and 15 compressors 204, between 3 and 12 compressors 204, between 3 and 9 compressors 204, between 3 and 6 compressors 204, between 5 and 20 compressors 204, between 5 and 17 compressors 204, between 5 and 15 compressors 204, between 5 and 12 compressors 204, between 5 and 12 compressors 204, or between 5 and 12 compressors 204. The compressors 204 may include 9 compressors 204, 5 to 6 compressors 204, 7 to 20 compressors 204, 7 to 17 compressors 204, 7 to 15 compressors 204, 7 to 12 compressors 204, 7 to 9 compressors 204, 9 to 20 compressors 204, 9 to 17 compressors 204, 9 to 15 compressors 204, 9 to 12 compressors 204, 11 to 20 compressors 204, 11 to 17 compressors 204, 11 to 15 compressors 204, 11 to 12 compressors 204, 13 to 20 compressors 204, 13 to 17 compressors 204, 13 to 15 compressors 204, 15 to 20 compressors 204, 15 to 17 compressors 204, or 17 to 20 compressors 204 (inclusive).In some embodiments, compressor train 202 includes at least two compressors 204, at least three compressors 204, at least four compressors 204, at least five compressors 204, at least six compressors 204, at least seven compressors 204, at least eight compressors 204, at least nine compressors 204, at least ten compressors 204, at least eleven compressors 204, at least 12 compressors 204, at least thirteen compressors 204, at least fourteen compressors 204, at least fifteen compressors 204, at least sixteen compressors 204, at least seventeen compressors 204, at least eighteen compressors 204, at least nineteen compressors 204, or at least twenty compressors 204. In some embodiments, compressor train 202 includes up to 2 compressors 204, up to 3 compressors 204, up to 4 compressors 204, up to 5 compressors 204, up to 6 compressors 204, up to 7 compressors 204, up to 8 compressors 204, up to 9 compressors 204, up to 10 compressors 204, up to 11 compressors 204, up to 12 compressors 204, up to 13 compressors 204, up to 14 compressors 204, up to 15 compressors 204, up to 16 compressors 204, up to 17 compressors 204, up to 18 compressors 204, up to 19 compressors 204, or up to 20 compressors 204.

[0072] In some embodiments, compressor train 202 includes m compressors 204, where m is, for example, an integer greater than 2. In some embodiments, m is greater than or equal to 2 and less than 21. Also, in some embodiments, m is selected for system 104 in response to one or more input parameters of system 104 (e.g., parameter 916 in FIG. 9 ) and / or one or more output parameters 916 of system 104. For example, in some embodiments, m is selected in response to the temperature of high-pressure steam 140 generated by system 104 and the temperature of hot water supplied to system 104 from facility 102 or another facility 102. In some embodiments, m is selected in response to the temperature rise (e.g., difference) between the temperature of high-pressure steam 140 generated by system 104 and the temperature of hot water supplied to system 104 from hot water source 110 associated with facility 102 or another facility 102. For example, in some embodiments, m is 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). , 60°F (15.6°C) ~ 205°F (96.1°C), 60°F (15.6°C) ~ 190°F (87.8°C), 60°F (15.6°C) ~ 175°F (7 9.4°C), 60°F(15.6°C)~150°F(65.6°C), 60°F(15.6°C)~135°F(57.2°C), 60°F(15.6°C)~1 20°F (48.9°C), 60°F (15.6°C) ~ 105°F (40.6°C), 60°F (15.6°C) ~ 90°F (32.2°C), 60°F (15. 6°C)~75°F(23.9°F), 80°F(26.7°C)~330°F(165°C), 80°F(26.7°C)~300°F(149°C), 80°F( 26.7°C)~270°F(135°C), 80°F(26.7°C)~250°F(121°C), 80°F(26.7°C)~220°F(65.6°C), 8 0°F (26.7°C) ~ 205°F (96.1°C), 80°F (26.7°C) ~ 190°F (87.8°C), 80°F (26.7°C) ~ 175°F (79.4°C)、80°F(26.7°C)~150°F(65.6°C)、80°F(26.7°C)~135°F(57.2°C)、80°F(26.7°C)~120°F(48.9°C)、80°F(26.7°C)~105°F(40.6°C)、80°F(26.7°C)~90°F(32.2°C)、100°F(37.8°C)~330°F(165°C)、100°F(37.8°C)~300°F(149°C)、100°F(37.8°C)~270°F(135°C)、100°F(37.8°C)~250°F(121°C)、100°F(37.8°C)~220°F(65.6°C)、100°F(37.8°C)~205°F(96.1°C)、100°F(37.8°C)~190°F(87.8°C)、100°F(37.8°C)~175°F(79.4°C)、100°F(37.8°C)~150°F(65.6°C)、100°F(37.8°C)~135°F(57.2°C)、100°F(37.8°C)~120°F(48.9°C)、100°F(37.8°C)~105°F(40.6°C)、120°F(48.9°C)~330°F(165°C)、120°F(48.9°C)~300°F(149°C)、120°F(48.9°C)~270°F(135°C)、120°F(48.9°C)~250°F(121°C)、120°F(48.9°C)~220°F(65.6°C)、120°F(48.9°C)~205°F(96.1°C)、120°F(48.9°C)~190°F(87.8°C)、120°F(48.9°C)~175°F(79.4°C)、120°F(48.9°C)~150°F(65.6°C)、120°F(48.9°C)~135°F(57.2°C)、140°F(60.0°C)~330°F(165°C)、140°F(60.0°C)~300°F(149°C)、140°F(60.0°C)~270°F(135°C)、140°F(60.0°C)~250°F(121°C)、140°F(60.0°C)~220°F(65.6°C)、140°F(60.0°C)~205°F(96.1°C)、140°F(60.0°C)~190°F(87.8°C)、140°F(60.0°C)~175°F(79.4°C)、140°F(60.0°C)~150°F(65.6°C), 175°F (79.4°C) ~ 330°F (165°C), 175°F (79.4°C) ~ 300°F (149°C), 175°F (79.4°C) ~ 270°F (135°C), 175°F (79.4°C) ~ 250°F (121°C), 175°F (79.4°C) ~ 220°F (65.6°C), 175°F (79.4°C) ~ 20 5°F (96.1°C), 175°F (79.4°C) ~ 190°F (87.8°C), 190°F (87.8°C) ~ 220°F (65.6°C), 190°F (87.8 °C)~330°F(165°C), 190°F(87.8°C)~300°F(149°C), 190°F(87.8°C)~270°F(135°C), 190°F(87 .8°C)~250°F(121°C), 190°F(87.8°C)~205°F(96.1°C), 205°F(96.1°C)~330°F(165°C), 205° F(96.1°C)~300°F(149°C), 205°F(96.1°C)~270°F(135°C), 205°F(96.1°C)~250°F(121°C), 20 Selected to achieve a temperature rise of 5°F (96.1°C) to 220°F (65.6°C), 250°F (121°C) to 330°F (165°C), 250°F (121°C) to 300°F (149°C), 250°F (121°C) to 270°F (135°C), or 270°F (135°C) to 330°F (165°C), inclusive. In some embodiments, m 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), 1 05°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 The temperature rise may be selected to achieve a temperature rise of 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), or at least 330°F (165°C). In some embodiments, m 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), at most 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), max 140°F (60.0°C), max 145°F (62.8°C), max 150°F (65.6°C), max 155°F (68.3°C), max 160°F (71.1°C), max 165°F (73.9°C), max 170°F (76.7°C) ), up to 175°F (79.4°C), up to 180°F (82.2°C), up to 185°F (85.0°C), up to 190°F (87.8°C), up to 195°F (90.6°C), up to 200°F (93.3°C), up to 205°F (96.1°C), up to 210°F (98.9°C), up to 215°F (102°C), up to 220°F (104°C), up to 250°F (121°C), up to 270°F (135°C), up to 300°F (149°C), or up to 330°F (165°C).

[0073] In some embodiments, a series of at least two compressors 204 are configured such that at least two are fluidly coupled in series. In some embodiments, at least a portion of a series of at least two compressors 204 are fluidly coupled in series, thereby allowing a medium flow from a first compressor 204-1 to a second compressor 204-2 of the series of at least two compressors 204. For example, in some embodiments, when a series of at least two compressors 204 are at least partially fluidly coupled in series, the flow path includes a path that passes through both the first compressor 204-1 and the second compressor 204-2. In some embodiments, a series of at least two compressors 204 are configured such that each compressor is arranged in a straight line, a substantially straight line, an arc, or a substantially arc. In some embodiments, a series of at least two compressors 204 are configured such that each compressor is arranged in a line, e.g., in an array including two or more parallel or substantially parallel lines. For example, in some embodiments, the series of at least two compressors 204 are configured to be aligned in a herringbone pattern, where a first line associated with a first set of compressors 204 in the series has a first slope, and a second set of compressors 204 has a second slope opposite the first slope. By way of non-limiting example, and referring briefly to FIG. 5C , in some embodiments, the series of at least two compressors 204 includes at least four compressors 204 (e.g., first compressor 204-1, second compressor 204-2, ..., compressor 204-m in FIG. 5B ). In some such embodiments, the at least four compressors 204 of the compressor train 202 are arranged in a herringbone array configuration such that the outlets of a first set of compressors 204 in the series of at least four compressors 204 have a first slope and a second set of compressors 204 have a second slope that is tangent, substantially tangential, perpendicular, or substantially perpendicular to the first slope. In some embodiments, the second slope is the reciprocal of the first slope. In some embodiments, the first slope and the second slope differ by 45 degrees or about 45 degrees.In some embodiments, the herringbone configuration of the compressor train 202 is configured so that vapor generated by each compressor 204 flows in a first direction. In some such embodiments, a first set of compressors 204 in the series of at least four compressors 204 are configured to redirect flow in a second direction and a second set of compressors 204 are configured to redirect flow in a third direction, the first, second, and third directions being different from one another. For example, in some embodiments, the herringbone configuration of the compressor train 202 is configured so that vapor generated by each compressor 204 flows in a first horizontal direction and a first set of compressors 204 in the series of at least four compressors 204 are configured to redirect flow in a second vertical direction and a second set of compressors 204 are configured to redirect flow in a third vertical direction, the second vertical direction being different from the third vertical direction. In some embodiments, the second vertical direction is against gravity (e.g., g in FIG. 5C has a vector direction going into the page of FIG. 5C ), and the third vertical direction is with gravity. However, the present disclosure is not limited thereto. For example, in some embodiments, the herringbone configuration of the compressor train 202 is configured so that the steam 140, 206 generated by each compressor 204 flows in a first horizontal direction, and in a series of at least four compressors 204, a first set of compressors 204 is configured to redirect the flow in a second horizontal direction and a second set of compressors 204 is configured to redirect the flow in a third horizontal direction, the second horizontal direction being different from the third horizontal direction. In some embodiments, the herringbone configuration is configured to maintain a constant or substantially constant height of the flow through the compressor train 204 so that a uniform or substantially uniform gravity force is applied to the compressor train 202. In some embodiments, the herringbone configuration of compressor train 202 is configured to provide aligned compressors arranged around a line (Y), with each compressor 204 in compressor train 202 positioned at a specific position around this line according to a first constant amplitude and a first constant frequency.For example, in some embodiments, the herringbone configuration of compressor train 202 is configured to provide aligned compressors arranged according to a function expressed as Y=B+(A*sin(k*X)). where Y is the first position of each compressor 204 in compressor train 202, B is the position of the end compressor 204 in compressor train 202, A is a constant amplitude, k is a constant frequency, and X is a second position of each compressor, although the present disclosure is not limited in this respect.

[0074] In some embodiments, compressor train 202 includes a first compressor 202-1 and a second compressor 202-2. First compressor 202-1 includes a first optimum inlet volumetric flow rate. In some such embodiments, second compressor 202-2 includes a second optimum inlet volumetric flow rate that is greater than the first optimum inlet volumetric flow rate of first compressor 202-1. In some such embodiments, first compressor 204-1 is coupled upstream of second compressor 204-2 in compressor train 202.

[0075] 2A and 2B, in some embodiments, the first compressor 204-1 is associated with a first size and the second compressor 204-2 is associated with a second size. In some embodiments, the second size is equal to the first size. Alternatively, in some embodiments, the second size is different from the first size. For example, in some embodiments, the first compressor 204-1 has a first diameter and the second compressor has a second diameter that is different from the first diameter. In some embodiments, the first diameter is larger than the second diameter. In some embodiments, the second diameter is the same as the first diameter. For example, in some embodiments, the first diameter is a number k selected from 0.1 meters to 1.6 meters, and the second diameter is a number l selected from 0.1 meters to 1.6 meters, where k and l are different numbers. However, the present disclosure is not limited in this respect. In some embodiments, the third compressor 204-3 has the second diameter and / or a third diameter that is larger than the second diameter. In some such embodiments, the third compressor is disposed upstream of the first compressor 204-1 and the second compressor 204-2. In some embodiments, the third compressor is disposed downstream of the first compressor 204-1 and upstream of the second compressor 204-2 such that the third compressor is interposed between and fluidly coupled to the first compressor 204-1 and the second compressor 204-2. In some embodiments, the third compressor is fluidly coupled in series to the first compressor 204-1 and the second compressor 204-2. However, the present disclosure is not limited in this respect.

[0076] In some embodiments, compressor train 202 includes a third compressor 204-3 adjacent to and interposed between first compressor 204-1 and second compressor 204-2. As a non-limiting example, and referring briefly to FIG. 4, compressor train 202 includes a second compressor 204-2 adjacent to and interposed between first compressor 204-1 and third compressor 204-3 of system 104 of FIG. 4. However, the present disclosure is not limited in this regard. In some embodiments, third compressor 204-3 includes either a first optimal inlet volumetric flow rate or a second optimal inlet volumetric flow rate.

[0077] In some embodiments, each compressor 204 in compressor train 202 has a compression ratio of less than 2.5. For example, in some embodiments, the compression ratio of each compressor 204 is defined by the ratio of the absolute discharge pressure to the absolute suction pressure of each compressor 204. In other words, in some such embodiments, the compression ratio of each compressor 204 is the ratio of the pressure at the inlet (e.g., inlet 224) of each compressor 204 to the pressure at the outlet of each compressor 204. Thus, the higher the compression ratio, the greater the pressure rise when compressing fluid through each compressor 204.

[0078] In some embodiments, the series of at least two compressors 204 includes one or more centrifugal compressors 204, one or more piston compressors 204, one or more rotary compressors 204, one or more screw compressors 204, or a combination thereof.

[0079] Further, in some embodiments, each of the series of at least two compressors 204 in compressor train 202 is a single-stage compressor 204. For example, in some embodiments, each stage of each compressor 204 is associated with a corresponding motor (e.g., power supply 986 in FIG. 9 ) and / or a corresponding variable frequency drive (VFD) controller (e.g., controller 906 in FIG. 9 ), thereby enabling each compressor 204 to operate individually and separately from the rest of the series of at least two compressors 204. In some embodiments, the impeller speed (e.g., rotational speed) is controlled by a controller (e.g., controller 906 in FIG. 9 ), which controls the impeller speed via a VFD associated with the corresponding motor. For example, in some embodiments, the impeller speed of each compressor 204 in compressor train 202 is individually controlled (e.g., by controller 906 in FIG. 9 ) to maintain a constant pressure supplying high-pressure steam 140 to the facility. However, the present disclosure is not limited in this respect.

[0080] In some embodiments, the controller 1906 is configured to vary the rotational speed of each of the series of at least two compressors 204 in the compressor train 202. For example, in some embodiments, the controller 1906 is configured to vary the rotational speed of each compressor 204 in the compressor train 202 to maintain a pressure at the outlet of the compressor train 202, such as to maintain an outlet pressure of the high-pressure steam 140 at least 80 PSI. However, the disclosure is not limited in this regard. For example, in some embodiments, the controller is configured to increase or decrease the rotational speed of the first compressor 202-1, increase or decrease the rotational speed of the second compressor 202-2, or a combination thereof (e.g., decrease the rotational speed of the first compressor 202-1 and increase the rotational speed of the second compressor 202-2, etc.). However, the disclosure is not limited in this regard.

[0081] Compressor train 202 also includes an inlet (e.g., first inlet 216-1 in any of FIGS. 2A-5B , etc.) that allows compressor train 202 to receive a flow of medium such as low-pressure steam generated in each flash vessel of flash vessel train 210 (e.g., first low-pressure steam 206-1 generated in first flash vessel 212-1 in any of FIGS. 2A-5B , second low-pressure steam 206-2 generated in second flash vessel 212-2 in any of FIGS. 2A-5B , ..., nth low-pressure steam 206-n generated in nth flash vessel 212-n, etc.).

[0082] Additionally, compressor train 202 includes an outlet (e.g., outlet 208 in any of FIGS. 2A-5B ). In some embodiments, outlet 208 of compressor train 202 is configured to supply high-pressure steam to facility 102. For example, in some embodiments, outlet 208 of compressor train 202 is configured to couple to an existing steam header in facility 102. This allows system 104 to supply high-pressure steam 140 without having to modify the configuration of facility 102, such as by adding a new steam header to facility 102.

[0083] 3A-5C, in some embodiments, the sizes of the three or more compressors 204 in the compressor train 202 decrease in a forward direction extending from the inlet to the outlet of the compressor train 202. In some embodiments, the upstream compressor in the compressor train 202 is located closer to the inlet than the downstream compressor, and the size of the upstream compressor is equal to or smaller than the size of the downstream compressor. In some embodiments, the sizes of the three or more compressors 204 in the compressor train 202 are the same in a direction extending from the inlet to the outlet of the compressor train. In some embodiments, the sizes of all compressors 204 in the compressor train 202 are equal to or smaller than a predetermined compressor size limit. In some embodiments, during design of the system 104, the number of compressors 204 in the compressor train 202 is determined based on steam parameters 116 (e.g., pressure and temperature) measured at the inlet and outlet of the compressor train 202. The sizes of the compressors 204 in the compressor train 202 increase in a reverse direction extending from the outlet to the inlet of the compressor train 202. The size of the portion of compressors 204 (e.g., two compressors) coupled to the inlet is equal to a predetermined compressor size limit. Following a determination that the portion of compressors 204 includes more than one compressor 204, one or more flash vessels 212 are added to facilitate a corresponding cascade compression process by the compressor train 202.

[0084] In some embodiments, the outlet of the compressor train 202 is configured to provide high-pressure steam 140 at a pressure between 50 PSI (3.44 Bar) and 315 PSI (21.7 Bar). For example, in some embodiments, the compressor train 202 may provide pressures between 50 PSI (3.44 Bar) and 300 PSI (20.7 Bar), between 50 PSI (3.44 Bar) and 275 PSI (19.0 Bar), between 50 PSI (3.44 Bar) and 250 PSI (17.2 Bar), between 50 PSI (3.44 Bar) and 225 PSI (15.5 Bar), between 50 PSI (3.44 Bar) and 200 PSI (13.8 Bar), between 50 PSI (3.44 Bar) and 175 PSI (12.1 Bar), between 50 PSI (3.44 Bar), and 250 PSI (17.2 Bar). )~150PSI(10.3Bar), 50PSI(3.44Bar)~125PSI(8.62Bar), 50PSI(3.44Bar)~100PSI(6.89Bar), 110PSI(7.58Bar)~315PSI(21.7Bar), 1 10PSI(7.58Bar)~300PSI(20.7Bar), 110PSI(7.58Bar)~275PSI(19.0Bar), 110PSI(7.58Bar)~250PSI(17.2Bar), 110PSI(7.58Bar)~225 PSI(15.5Bar), 110PSI(7.58Bar)~200PSI(13.8Bar), 110PSI(7.58Bar)~175PSI(12.1Bar), 110PSI(7.58Bar)~150PSI(10.3Bar), 110P SI(7.58Bar)~125PSI(8.62Bar), 170PSI(11.7Bar)~315PSI(21.7Bar), 170PSI(11.7Bar)~300PSI(20.7Bar), 170PSI(11.7Bar)~275PSI (19.0Bar), 170PSI(11.7Bar)~250PSI(17.2Bar), 170PSI(11.7Bar)~225PSI(15.5Bar), 170PSI(11.7Bar)~200PSI(13.8Bar), 170PSI(1 1.7Bar)~175PSI(12.1Bar), 230PSI(15.6Bar)~315PSI(21.7Bar), 230PSI(15.6Bar)~300PSI(20.7Bar), 230PSI(15.6Bar)~275PSI(19.230 PSI (15.6 Bar) to 250 PSI (17.2 Bar), 290 PSI (20.0 Bar) to 315 PSI (21.7 Bar), or 290 PSI (20.0 Bar) to 300 PSI (20.7 Bar), inclusive. In some embodiments, compressor train 202 is configured to supply high-pressure steam 140 to an existing steam header of facility 102 at a pressure of at least 50 PSI (3.44 Bar), at least 70 PSI (4.83 Bar), at least 90 PSI (6.21 Bar), at least 110 PSI (7.58 Bar), at least 130 PSI (8.96 Bar), at least 150 PSI (10.3 Bar), 170 PSI (11.7 Bar), at least 190 PSI (13.1 Bar), at least 210 PSI (14.5 Bar), at least 230 PSI (15.6 Bar), at least 250 PSI (17.2 Bar), at least 270 PSI (18.6 Bar), at least 290 PSI (20.0 Bar), or at least 310 PSI (21.4 Bar). In some embodiments, the compressor train 202 provides a pressure of at least 50 PSI (3.44 Bar), at least 70 PSI (4.83 Bar), at least 90 PSI (6.21 Bar), at least 110 PSI (7.58 Bar), at least 130 PSI (8.96 Bar), at least 150 PSI (10.3 Bar), 170 PSI (11.7 Bar), at least 190 PSI (13.1 Bar), at least 210 PSI (14.5 Bar), at least 230 PSI (15.6 Bar), at least 250 PSI (17.2 Bar), at least 270 PSI (18.6 Bar), at least 290 PSI (20.0 Bar), or at least 310 PSI (21.The system 104 is configured to supply high-pressure steam 140 to an existing steam header of the facility 102 at a pressure of 100 bar (4 bar). Thus, the system 104 can supply high-pressure steam 140 to the facility 102 at a sufficient pressure such that the facility 102 can directly utilize the high-pressure steam 140. In some embodiments, all pressures referred to in this paragraph are quoted as gauge pressures. In some embodiments, pressures referred to in this disclosure are gauge pressures unless expressly stated otherwise.

[0085] System 104 further includes a flash vessel train (e.g., flash vessel train 210 of any of Figures 2A-5B, etc.) that includes a series of at least two flash vessels (e.g., first flash vessel 212-1 of any of Figures 2A-5B, second flash vessel 212-2 of any of Figures 2A-5B, ..., flash vessel 212-n of Figure 5B, etc.). For example, in some embodiments, the flash vessel train 210 may include between 2 and 20 flash vessels 212, between 2 and 17 flash vessels 212, between 2 and 15 flash vessels 212, between 2 and 12 flash vessels 212, between 2 and 9 flash vessels 212, between 2 and 6 flash vessels 212, between 2 and 3 flash vessels 212, between 3 and 20 flash vessels 212, between 3 and 17 flash vessels 212, between 3 and 15 flash vessels 212, between 3 and 12 flash vessels 212, between 3 and 9 flash vessels 212, between 3 and 6 flash vessels 212, between 5 and 20 flash vessels 212, between 5 and 17 flash vessels 212, between 5 and 15 flash vessels 212, between 5 and 12 flash vessels 212, between 5 and 9 flash vessels 212, between 5 and 6 flash vessels 212, 12, 7 to 20 flash vessels 212, 7 to 17 flash vessels 212, 7 to 15 flash vessels 212, 7 to 12 flash vessels 212, 7 to 9 flash vessels 212, 9 to 20 flash vessels 212, 9 to 17 flash vessels 212, 9 to 15 flash vessels 212, 9 to 12 flash vessels 212, 11 to 20 flash vessels 212, 11 to 17 flash vessels 212, 11 to 15 flash vessels 212, 11 to 12 flash vessels 212, 13 to 20 flash vessels 212, 13 to 17 flash vessels 212, 13 to 15 flash vessels 212, 15 to 20 flash vessels 212, 15 to 17 flash vessels 212, or 17 to 20 flash vessels (inclusive).In some embodiments, flash vessel train 210 includes at least two flash vessels 212, at least three flash vessels 212, at least four flash vessels 212, at least five flash vessels 212, at least six flash vessels 212, at least seven flash vessels 212, at least eight flash vessels 212, at least nine flash vessels 212, at least ten flash vessels 212, at least eleven flash vessels 212, at least twelve flash vessels 212, at least thirteen flash vessels 212, at least fourteen flash vessels 212, at least fifteen flash vessels 212, at least sixteen flash vessels 212, at least seventeen flash vessels 212, at least eighteen flash vessels 212, at least nineteen flash vessels 212, or at least twenty flash vessels 212. In some embodiments, flash vessel train 210 includes up to two flash vessels 212, up to three flash vessels 212, up to four flash vessels 212, up to five flash vessels 212, up to six flash vessels 212, up to seven flash vessels 212, up to eight flash vessels 212, up to nine flash vessels 212, up to ten flash vessels 212, up to eleven flash vessels 212, up to twelve flash vessels 212, up to thirteen flash vessels 212, up to fourteen flash vessels 212, up to fifteen flash vessels 212, up to sixteen flash vessels 212, up to seventeen flash vessels 212, up to eighteen flash vessels 212, up to nineteen flash vessels 212, or up to twenty flash vessels 212. However, the disclosure is not limited in this respect. For example, and referring briefly to Figure 5C, in some embodiments, flash vessel train 210 includes a flash vessel 212 that is an end flash vessel 212. In some embodiments, flash vessel train 210 consists of one flash vessel 212.

[0086] In some embodiments, there is a one-to-one relationship between each compressor 204 in compressor train 202 and each flash vessel 212 in flash vessel train 210. For example, briefly referring to FIG. 2A , system 104 illustrates a one-to-one relationship between each compressor 204 in compressor train 202 and each flash vessel 212 in flash vessel train 210, in that compressor train 202 has two compressors 204 and flash vessel train 210 similarly has two flash vessels 212. In some embodiments, there is a one-to-one relationship between a compressor 204 and a flash vessel 212 when the temperature difference between a first compressor and a second compressor meets a threshold temperature, such as 10° C., 20° C., etc. In some embodiments, there is a one-to-one relationship between a compressor 204 and a flash vessel 212 when the temperature difference between a first flash vessel and a second flash vessel meets a threshold temperature, such as 20° C. Thus, in some embodiments, compressor train 202 includes p compressors (e.g., first compressor 204-1, second compressor 204-2, ..., pth compressor 204-p), and flash vessel train 210 includes p flash vessels 212 (e.g., first flash vessel 212-1, second flash vessel 212-2, ..., pth flash vessel 212-p), where p is an integer (i) greater than or equal to 2 and (ii) less than or equal to 20. In some embodiments, p is an integer (i) greater than 2 and (ii) less than or equal to 20. However, the present disclosure is not limited in this respect. In some embodiments, each compressor 204 in compressor train 202 and each flash vessel 212 in flash vessel train 210 have a many-to-one relationship. As another non-limiting example, and referring briefly to FIG. 4 , system 104 illustrates a many-to-one relationship between each compressor 204 in compressor train 202 and each flash vessel 212 in flash vessel train 210, in that compressor train 202 has three compressors 204, while flash vessel train 210 has two flash vessels 212.For example, in some embodiments, a many-to-one relationship is formed when the first size of the first compressor 204 is the same as the second size of the second compressor 204, and a first flash vessel 212 is interposed between the first compressor 204 and the second compressor 204. Thus, in some such embodiments, the compressor train 202 includes m compressors 204 (e.g., first compressor 204-1, second compressor 204-2, ..., mth compressor 204-m), and the flash vessel train 210 includes n flash vessels 212 (e.g., first flash vessel 212-1, second flash vessel 212-2, ..., nth flash vessel 212-n), where m and n are each an integer that is (i) greater than or equal to 2 and (ii) less than or equal to 20, and m is greater than n.

[0087] Similar to the series of at least two compressors 204 of compressor train 202, the series of at least two flash vessels 212 of flash vessel train 210 are at least partially fluidly coupled in series, thereby allowing a flow of medium to flow from one to the other of the series of at least two flash vessels 212. For example, in some embodiments, and briefly referring to FIG. 2A , the series of at least two flash vessels 212, when at least partially fluidly coupled in series, includes a path through both the second inlet 224-2 of the second flash vessel 212-2, the second liquid outlet 228-2 of the second flash vessel, and the first inlet 224-1 of the first flash vessel 212-1 of flash vessel train 210.

[0088] Thus, the series of at least two flash vessels 212 includes a terminal flash vessel 212 located at one end of the flash vessel train 210. For example, with brief reference to Figure 2A, the first flash vessel 212-1 is the first terminal flash vessel 212 of the series of at least two flash vessels 212 located at one end of the flash vessel train 210, and the second flash vessel 212-2 is the second terminal flash vessel 212 of the series of at least two flash vessels 212 located at a second end of the flash vessel train 210. As another non-limiting example, with brief reference to Figure 5A, the first flash vessel 212-1 is the first terminal flash vessel 212 of the series of at least two flash vessels 212 located at one end of the flash vessel train 210, and flash vessel 212-n is the second terminal flash vessel 212 of the series of at least two flash vessels 212 located at a second end of the flash vessel train 210. Thus, by fluidly arranging at least two flash vessels 212 in series, flash vessel train 210 can utilize thermal energy from steam condensate (such as, for example, steam condensate 214 in any of Figures 2A-5B), although the present disclosure is not limited in this respect.

[0089] In some embodiments, each of the series of at least two flash vessels 212 is configured (e.g., by control module 906 of FIG. 9 ) to maintain a predetermined internal pressure or a predetermined range of internal pressures that is lower than the saturation pressure of the hot water received by system 104. For example, in some embodiments, each flash vessel 212 is configured to maintain an internal pressure that is lower than the saturation pressure of the hot water received at inlet 224 into the respective flash vessel 212. Each of the series of at least two flash vessels 212 is also configured to expand the hot water received at inlet 224 of the flash vessel 212 to produce low-pressure steam (e.g., first low-pressure steam 206-1 produced at first flash vessel 212-1 in any of FIGS. 2A-5B , second low-pressure steam 206-2 produced at second flash vessel 212-2 in FIG. 2A in any of FIGS. 2A-5B , ..., nth low-pressure steam 206-n produced at nth flash vessel 212-n, etc.). For example, in some embodiments, the internal pressure of each flash vessel 212 in the flash vessel train 210 is determined based on a first temperature of the hot water received by the system 104 or a second temperature of the condensate received by the respective flash vessel 212 (e.g., steam condensate 214 in FIG. 4 , steam outlet 228-2 in FIG. 2A , etc.). As a non-limiting example, in some embodiments, the hot water source 110 provides hot water at a temperature of 120°F, and the terminal flash vessel 212-1 in the flash vessel train 210 is configured to have an internal pressure of approximately 88 millibars absolute (mBara), which is the saturation pressure of water at 110°F. However, the present disclosure is not limited in this respect. In some embodiments, the internal pressure of each flash vessel 212 is less than the saturation temperature of the media received by the flash vessel, such as the liquid received from the liquid outlet 228 of an adjacent flash vessel 212 or the hot water received from the hot water source 110.As a result, each of the series of at least two flash vessels 212 is configured to maintain a predetermined internal pressure or a predetermined internal pressure range that is less than the saturation pressure of the hot water received by the system 104, allowing the system 104 to not only be connected to various facilities 303 with different hot water source 110 temperatures, but also to adapt in real time to changes in operating parameters 916 at each facility 102 connected to the system 104.

[0090] In some embodiments, one or more flash vessels 212 in the flash vessel train 210 are positioned above an inlet of the flash vessel train 210 (e.g., second inlet 224-2 in any of FIGS. 2A-5B ) such that each flash vessel train 210 is elevated or substantially elevated from inlet 224-2 of the flash vessel train 210, thereby effectively increasing the potential energy of each of the one or more flash vessels 212. By positioning one or more flash vessels 212 in the flash vessel train 210 above inlet 224-2 of the flash vessel train 210, the system 104 is configured to utilize additional potential energy available from the pressure differential between the elevation of inlet 224-2 of the flash vessel train 210 and one or more flash vessels 212. Such a configuration also enables the system 104 to minimize power consumption (e.g., the power consumption of the power supply 986 in FIG. 9 required to operate the repressurization pump 220 in FIG. 2A ) when receiving cooling water produced in each of the one or more flash vessels 212 in the flash vessel train 210.

[0091] Thus, in some embodiments, each of the series of at least two flash vessels 212 includes two or more outlets. For example, in some embodiments, a vapor outlet (e.g., vapor outlet 226-1 of flash vessel 212-1 in any of Figures 2A-5B, vapor outlet 226-2 of flash vessel 212-2 in any of Figures 2A-5B, ..., vapor outlet 226-n of flash vessel 212-n in Figure 5A, etc.) is configured to transport low-pressure vapor 206 produced in the flash vessel 212 to compressor 204 of compressor train 202. For example, in some embodiments, first vapor outlet 226-1 of terminal flash vessel 212-1 is fluidly coupled to inlet 216-1 of compressor train 202.

[0092] Additionally, system 104 includes a vapor outlet 226 of the remainder of the series of at least two flash vessels 212 fluidly coupled between the series of at least two compressors 204 of compressor train 202. As a non-limiting example, and with brief reference to Figures 2A and 4, second vapor outlet 226-2 of second flash vessel 212-2 is fluidly coupled to second inlet 216-2 of second compressor 204-2 in compressor train 202. As yet another non-limiting example, and with brief reference to Figure 3, second vapor outlet 226-2 of second flash vessel 212-2 is fluidly coupled to third inlet 216-3 of third compressor 204-3 in compressor train 202.

[0093] In some embodiments, the flash vessel train 210 further includes an inlet for the flash vessel train 210 (e.g., second inlet 224-2 of the first flash vessel 212-1 in FIG. 5A , etc.). The inlet 224 of the flash vessel train 210 is configured to receive hot water from a facility 102 (e.g., hot water source 110 of any of FIGS. 1-5 ). For example, in some embodiments, the inlet 224 of the flash vessel train 210 is configured to receive hot water from the hot water source 110 from the same facility 102 (e.g., first facility 102-1 in FIG. 1B ) that receives the high-pressure steam 140 from the system 104, or to receive hot water from the hot water source 110 from another facility 102 (e.g., second facility 102-2 in FIG. 1A ). In some embodiments, the other facility 102 providing the hot water from the hot water source 110 is independent of the use of the high-pressure steam 140 generated in the system 104. However, the present disclosure is not limited in this respect. Furthermore, in some such embodiments, utilizing hot water as the flowing medium within system 104 (e.g., as a refrigerant for system 104) increases the efficiency of system 104 because water has zero global warming potential (0 GWP), is non-flammable, non-toxic, and poses no regulatory risks, in contrast to other conventional refrigerants such as hydrofluorocarbons (HFCs) and / or hydrofluoroolefins (HFOs), which are toxic and / or flammable.

[0094] In some embodiments, the inlet 224 of the flash vessel train 210 is the inlet of the terminal flash vessel 212-1 of the flash vessel train 210. For example, in some embodiments, the second inlet 224-2 of the terminal flash vessel 212-1 is configured to receive hot water from the hot water source 110, and the hot water is supplied to the interior of the terminal flash vessel 212-1.

[0095] In some embodiments, the remainder of the series of at least two flash vessels 212 each include a liquid outlet (such as, for example, second liquid outlet 228-2 in any of Figures 2-5). Each liquid outlet 228 of the remainder of the series of at least two flash vessels 212 is fluidly coupled to the inlet 224 of another flash vessel 212 in the series of at least two flash vessels 212. As a non-limiting example, and referring briefly to Figure 2A, the second flash vessel 212-2 is not the terminal flash vessel 212-1 of the flash vessel train 210 and corresponds to the remainder of the series of at least two flash vessels 212 because it includes a second liquid outlet 228-2 fluidly coupled to the inlet 224-1 of the terminal flash vessel 212-1 of the series of at least two flash vessels 212.

[0096] In some embodiments, the end flash vessel 212-1 includes a liquid outlet (such as, for example, the first liquid outlet 228-1 in any of FIGS. 2-5 ) fluidly coupled to the outlet of the system 104. As a non-limiting example, in some embodiments, the outlet of the system 104 is a cooling water source (such as, for example, the cooling water source 120 in any of FIGS. 1-7 ) associated with a first facility 102-1 that receives the high-pressure steam 140 generated by the system 104, or a second facility 102-2 that is associated with hot water received by the system 104 from the hot water source 110. For example, in some embodiments, the outlet of the cooling water source 120 of the system 104 is fluidly coupled to the hot water of the hot water source 110 received from the facility 102 or another facility 102. Thus, in some such embodiments, the cooling water source outlet 120 of the system 104 is configured as a cooling water source for closed-loop cooling water treatment associated with the facility that provides the hot water source 110. Furthermore, in some embodiments, the system 104 can operate at the unique operating conditions of each facility 102 without substantial modifications by connecting only to the existing steam header and cooling water source 120 of the same facility 102.

[0097] In some embodiments, the liquid outlet 228-1 of the end-of-line flash vessel 212-1 is fluidly coupled to a repressurization pump (e.g., the repressurization pump 220 of any of FIGS. 2-5). The repressurization pump 220 is coupled to the outlet 120 of the cooling water source of the system 104, interposed between the liquid outlet 228 of the end-of-line flash vessel 212-1. This allows the repressurization pump 220 to convey the fluid produced in the end-of-line flash vessel 212-1 to the outlet of the cooling water source 120 of the system 104 when a pressure gradient exists between the pressure of the fluid produced in the end-of-line flash vessel 212-1 and the outlet of the cooling water source 120 of the system 104. For example, in some embodiments, the repressurization pump 220 is configured to generate a negative pressure gradient to receive the cooling water produced in the flash vessel 212 from the liquid outlet 228 of the flash vessel 212, e.g., to maintain a steady state of the flash vessel 212. However, the present disclosure is not limited in this respect. In some embodiments, the repressurization pump 220 is configured to maintain the pressure at the liquid outlet 228 of the flash vessel 212 at a predetermined pressure or within a predetermined pressure range.

[0098] In some embodiments, the system 104 includes one or more valves (e.g., the first valve 218-1 in any of Figures 2-5, the second valve 218-2 in any of Figures 2A-5B, the third valve 218-3 in Figure 5A, the fourth valve 218-4 in Figure 5A, ..., the nth valve 218-n in Figure 5A, etc.), each of which is configured to control (e.g., stop and / or delay) the flow of medium through the valve 218 (e.g., the flow rate of hot water received from the hot water source 110, the flow rate of low-pressure steam 206, the flow rate of cooling water, etc.) that is ultimately received by or from each flash vessel 212. In some embodiments, one of the one or more valves 218 is located upstream of an inlet (e.g., first inlet 224-1 in FIG. 5A , second inlet 224-2 in FIG. 5A , etc.) of the respective flash vessel 212 or downstream of an outlet (e.g., vapor outlet 226 or liquid outlet 228) of the respective flash vessel 212. In some embodiments, each valve 218 is configured to meter the flow rate of a medium received at or from the respective flash vessel 212 (e.g., the flow rate of hot water received from hot water source 110, the flow rate of low-pressure steam 206, the flow rate of cooling water, etc.).

[0099] In some embodiments, the system 104 further includes a controller (e.g., control module 906 of FIG. 9 ). In some embodiments, the controller 906 is configured to maintain a temperature range for the flash vessel train 210, such as maintaining the temperature of the high-pressure steam 140 generated by the system 104 and / or the temperature of an outlet of the system 104 (e.g., an outlet of the cooling water source 120 associated with the facility 102).

[0100] In some embodiments, the controller 906 is configured to prevent stalling or surging in each centrifugal compressor 204 in the compressor train 202. For example, in some embodiments, the controller 906 is configured to determine whether the mass flow rate associated with each centrifugal compressor 204 in the compressor train 202 satisfies a first threshold mass flow rate associated with a stonewall condition for the flow in each centrifugal compressor 204 and / or a second threshold mass flow rate associated with a surge condition for the flow in each centrifugal compressor 204. However, the present disclosure is not limited in this respect. As a non-limiting example, each compressor 204 has a minimum mass flow rate at which it can stably operate, i.e., a surge condition.

[0101] In some embodiments, the system 104 further includes an attemperator train (e.g., attemperator train 230 of FIG. 5A, etc.). In some embodiments, the attemperator train 230 includes at least one attemperator (e.g., first attemperator 232-1, 232-2, ..., 232-q of FIG. 5A, etc.). For example, in some embodiments, the attemperator train 230 may include 2 to 20 attemperators 232, 2 to 17 attemperators 232, 2 to 15 attemperators 232, 2 to 12 attemperators 232, 2 to 9 attemperators 232, 2 to 6 attemperators 204, 2 to 3 attemperators 232, 3 to 20 attemperators 232, 3 to 17 attemperators 232, 3 to 15 attemperators 232, 3 to 12 attemperators 232, 3 to 9 attemperators 232, 3 to 6 attemperators 232, 5 to 20 attemperators 232, 5 to 17 attemperators 232, 5 to 15 attemperators 232, 5 to 12 attemperators 232, 5 to 9 attemperators 232, 5 to 6 attemperators 232, 7 The number of attenuators 232 may be up to 20, 7 to 17 or less attenuators 232, 7 to 15 attenuators 232, 7 to 12 attenuators 232, 7 to 9 attenuators 232, 9 to 20 attenuators 232, 9 to 17 attenuators 232, 9 to 15 attenuators 232, 9 to 12 attenuators 232, 11 to 20 attenuators 232, 11 to 17 attenuators 232, 11 to 15 attenuators 232, 11 to 12 attenuators 232, 13 to 20 attenuators 232, 13 to 17 attenuators 232, 13 to 15 attenuators 232, 15 to 20 attenuators 232, 15 to 17 attenuators 232, or 17 to 20 attenuators 232 (inclusive).In some embodiments, compressor train 202 includes at least two attemperators 232, at least three attemperators 232, at least four attemperators 232, at least five attemperators 232, at least six attemperators 232, at least seven attemperators 232, at least eight attemperators 232, at least nine attemperators 232, at least ten attemperators 232, at least eleven attemperators 232, at least twelve attemperators 232, at least thirteen attemperators 232, at least fourteen attemperators 232, at least fifteen attemperators 232, at least sixteen attemperators 232, at least seventeen attemperators 232, at least eighteen attemperators 232, at least nineteen attemperators 232, or at least twenty attemperators 232. In some embodiments, compressor train 202 includes up to 2 attemperators 232, up to 3 attemperators 232, up to 4 attemperators 232, up to 5 attemperators 232, up to 6 attemperators 232, up to 7 attemperators 232, up to 8 attemperators 232, up to 9 attemperators 232, up to 10 attemperators 232, up to 11 attemperators 232, up to 12 attemperators 232, up to 13 attemperators 232, up to 14 attemperators 232, up to 15 attemperators 232, up to 16 attemperators 232, up to 17 attemperators 232, up to 18 attemperators 232, up to 19 attemperators 232, or up to 20 attemperators 232.

[0102] Each attemperator 232 in attemperator train 230 includes an outlet configured to inject hot water received from the facility 102 or another facility 102 into compressor train 202. For example, in some embodiments, each attemperator 232 in attemperator train 230 is configured to receive a portion of the hot water from hot water source 110 that is supplied to inlet 224-2 of terminal flash vessel 212-1. This allows attemperator train 230 to utilize the same source of hot water from hot water source 110. However, the disclosure is not limited in this respect. In some embodiments, each attemperator 232 in attemperator train 230 is configured to remove heat (e.g., superheat) added to low-pressure steam 206 by each compressor 204 of compressor train 202 by injecting hot water from hot water source 110 into the low-pressure steam 206 between compressors 204. Thus, in some such embodiments, the vaporization of water injected by attemperator 232 removes superheat from low-pressure steam 206, thereby increasing the mass flow rate of low-pressure steam 206 through system 104. In some embodiments, attemperator train 230 is configured to eliminate the need for an intercooler in each compressor 204 of compressor train 202. Also, in some embodiments, attemperator train 230 may be used to remove heat from low-pressure steam 206 as it is compressed by compressor 204, thereby increasing the efficiency of system 104. This allows system 104 to operate at or near the water saturation line without intercooler heat losses or significant entropy losses due to superheat.

[0103] In some embodiments, there is a one-to-one relationship between each compressor 204 in compressor train 202 and each attemperator 232 in attemperator train 230. For example, briefly referring to Figure 5A, system 104 illustrates a one-to-one relationship between each compressor 204 in compressor train 202 and each attemperator 232 in attemperator train 230, in that compressor train 202 has four compressors 204 and attemperator train 230 similarly has four attemperators 232. Thus, in some embodiments, compressor train 202 includes m compressors (e.g., first compressor 204-1, second compressor 204-2, ..., mth compressor 204-m in FIG. 5A ), and attemperator train 230 includes q attemperators 232 (e.g., first attemperator 231-1, second attemperator 232-2, ..., qth attemperator 231-q in FIG. 5A ), where m and q are the same integer (i) greater than or equal to 2 and (ii) less than or equal to 20. In some embodiments, m and q are the same integer (i) greater than or equal to 2 and (ii) less than or equal to 20. However, the present disclosure is not limited in this regard. In some embodiments, each compressor 204 in compressor train 202 and each attemperator 232 in attemperator train 230 have a many-to-one relationship. Thus, in some such embodiments, compressor train 202 includes m compressors and attemperator train 230 includes q attemperators 232, where m and q are each an integer that is (i) greater than or equal to 2 and (ii) less than or equal to 20, and m is greater than q. However, the present disclosure is not limited in this regard.

[0104] In some embodiments, the system 104 has a coefficient of performance (COP) greater than 65% of the corresponding Carnot efficiency. The Carnot efficiency represents the highest possible efficiency of a heat pump system operating between a high-temperature source and a low-temperature source. For example, in some embodiments, a heat pump system 104 operating between two sources of different thermal temperatures (e.g., a high-temperature hot water source 110 and a low-temperature chilled water source 120, a low-temperature hot water source 110 and high-temperature high-pressure steam, a high-temperature high-pressure steam and a low-temperature chilled water source 120, or a combination thereof) has an associated efficiency rating determined by a coefficient of performance (COP), energy efficiency ratio (EER), or the like. In some embodiments, the COP is determined by the amount of heat transferred from the low-temperature source divided by the network input, i.e., the amount of heat transferred to the high-temperature source minus the refrigerant effectiveness value. For example, in some embodiments, the COP of the system 104 is determined by the temperature of the high-pressure steam 140 produced by the system 104 and the temperature of the hot water source 110 that supplies the hot water received by the system. In some embodiments, the COP of the system 104 is a function of the ratio of the power consumption of the system 104 to the output heat power of the system 104. In some embodiments, the corresponding Carnot efficiency ratio is a function of the ratio of the Carnot COP to the actual COP of the system 104. Further details and information regarding the COP and / or Carnot efficiency of heat pump systems can be found in the printed version of "Marks' Standard Handbook for Mechanical Engineers" by Sadegh et al. (2018, McGraw-Hill Education), which is incorporated herein by reference in its entirety for all purposes.

[0105] In some embodiments, the flash vessel 212 in the flash vessel train 210 includes a blowdown (e.g., blowdown 170 in FIG. 1A or 5B ). In some embodiments, the blowdown 170 is configured to remove contaminants contained in the flash vessel 212. For example, in some embodiments, the blowdown 170 is configured to continuously remove contaminants contained in the flash vessel 212 (e.g., continuous blowdown 170) or to intermittently remove contaminants contained in the flash vessel 212. For example, in some embodiments, the contaminants include one or more fluids and / or one or more solids that are at least partially removed from the system 104 by the discharge of the blowdown 170. This prevents the contaminants from affecting heat transfer efficiency of the system 104 and downstream components of the flash vessel 212. In some embodiments, the contaminants do not include or are substantially free of steam (e.g., low-pressure steam 206, high-pressure steam 140, etc.). In some embodiments, by removing contaminants via blowdown 170, flash vessel 212 can further receive hot water from hot water source 110, such as make-up hot water from hot water source 110, and can generate high-pressure steam 140 via compressor train 202. Also, in some embodiments, blowdown 170 is configured to remove at least a portion of the contaminants at a temperature below the first temperature of the hot water, thereby completing the removal without causing heat loss to system 104. However, the disclosure is not limited in this respect. In some embodiments, blowdown 170 is configured to continuously remove contaminants without an active control mechanism (e.g., without receiving one or more instructions from controller 906). For example, in some embodiments, blowdown 170 is in electrical communication with a sensor 982, such as a conductivity sensor 982, configured to detect one or more contaminants in flash vessel 212. This sensor 982 provides feedback information to blowdown 170 regarding the status of the one or more contaminants.

[0106] In some embodiments, blowdown 170 is associated with a second liquid outlet of a corresponding flash vessel 212 in flash vessel train 210. In some embodiments, blowdown 170 is fluidly configured to selectively remove fluid from a corresponding flash vessel 212.

[0107] In some embodiments, the controller 906 is in electrical communication with the second liquid outlet of the corresponding flash vessel 212. In some embodiments, the controller is configured to control the selective removal of fluid.

[0108] In some embodiments, a flash vessel 212 in the flash vessel train 210 includes a degasser (e.g., degasser 240 in FIG. 5B ). In some embodiments, the degasser 240 is configured to form an outlet for the flash vessel 212, such as a second liquid outlet for the flash vessel 212. In some embodiments, the degasser 240 is configured to selectively remove fluid from the corresponding flash vessel 412. For example, in some embodiments, the degasser 240 is configured to vary the opening of the outlet for the flash vessel 212 according to a determined threshold amount of the first medium (e.g., contaminants in the flash vessel, hot water in the flash vessel, steam in the flash vessel, etc.), thereby selectively removing fluid from the corresponding flash vessel 212. In some such embodiments, the fluid removed from the corresponding flash vessel 212 includes one or more gases (e.g., oxygen, carbon dioxide, etc.) contained in the flash vessel 212 and / or one or more liquids contained in the flash vessel 212. However, the present disclosure is not limited thereto. In some embodiments, controller 1906 of system 104 is in electrical communication with a second liquid outlet associated with degasser 240. In some such embodiments, controller 1906 is configured to selectively allow fluid communication between the second liquid outlet and an outlet of system 104, thereby allowing liquid to be removed from flash vessel 212. In some embodiments, controller 906 is configured to vary the flow rate of fluid through attemperator 232 in accordance with a determination that the temperature and / or pressure associated with compressor train 202 meets a threshold pressure and / or temperature. As a non-limiting example, in some embodiments, controller 906 is configured to vary the size of the second outlet, e.g., the diameter of the opening or aperture at the outlet of attemperator 232.For example, in some embodiments, pursuant to a determination that the threshold pressure is not met because the pressure associated with compressor 204 is less than the threshold pressure, the controller is configured to reduce the size (e.g., diameter of the opening) of the second outlet to increase the internal pressure of system 104 and / or to modify the mass flow rate of fluid output by attemperator 232. However, the present disclosure is not limited in this respect.

[0109] In some embodiments, system 104 further includes one or more boilers (e.g., boiler 236 in FIG. 5A ). Boiler 236 is interposed between and fluidly coupled to outlets 208 of compressor train 202. In some embodiments, boiler 236 is configured to remove moisture or condensate from high-pressure steam 140 generated by compressor train 202. For example, in some embodiments, boiler 236 is configured to heat high-pressure steam, for example, to generate superheated steam. In some embodiments, boiler 236 is configured to provide auxiliary steam to meet peak steam demands from facility 102 that cannot be met solely by the steam generation capacity of compressor train 202. In some embodiments, boiler 236 is configured to function as a backup source for generating steam for use by facility 102 in the event that compressor train 202 is intentionally or unintentionally powered off. However, the present disclosure is not limited in this respect.

[0110] In some embodiments, system 104 further includes a vapor accumulator (e.g., vapor accumulator 238 in FIG. 5A ). Vapor accumulator 238 is interposed between and fluidly coupled to outlets 208 of compressor train 202. For example, in some embodiments, vapor accumulator 238 is configured to increase the storage capacity of system 104, thereby enabling system 104 to accommodate fluctuations (e.g., one or more peaks and / or one or more valleys) in the facility's demand for high-pressure steam 140 generated by system 104.

[0111] The systems, methods, and apparatus of the present disclosure have other features and advantages that will become apparent from, or are further described in detail in, the accompanying drawings and the following detailed description, which together serve to explain certain principles of the invention.

[0112] FIG. 6 is a chart illustrating various parameters associated with various high-pressure steam generating heat pump systems, according to some embodiments. Referring to FIG. 6, in some embodiments, the systems, methods, and apparatuses of the present disclosure provide a plurality of heat pump systems 104. In some embodiments, each of the plurality of heat pump systems 104 is configured to achieve a unique set of parameter requirements. In some embodiments, the set of unique parameter requirements (e.g., parameters 916 in FIG. 9 ) included the output pressure of high-pressure steam generated by each system 104, the output flow rate of high-pressure steam generated by each system 104, and the temperature of the hot water source 110 received by each system 104. In some embodiments, the remainder of the parameters 916 are held constant across each heat pump system 104 or are derived directly from the set of unique parameters 916 associated with each system 104.

[0113] Furthermore, the disclosed systems, methods, and apparatus avoid the losses associated with an intermediate refrigerant and heat transfer to and / or from the intermediate refrigerant. Rather, the disclosed systems, methods, and apparatus generate high-pressure steam directly from the hot water source 110 and directly compress the low-pressure steam generated in the flash vessel train 210 using a multi-stage mechanical vapor recompression (MVR) compressor train 202 having a series of at least two centrifugal compressors 204. In some embodiments, the system 104 includes an attemperator train 230 including an attemperator 232 disposed between each compressor 204 in the compressor train 202.

[0114] Thus, in some embodiments, the systems, methods, and apparatus of the present disclosure achieve a high COP (e.g., COP4.5, COP4.0, etc.) by leveraging the high efficiency of utilizing one or more centrifugal compressors 204 in the compressor train 202 and avoiding superheat losses due to high compression ratio compressors 204 commonly found in conventional high temperature industrial heat pump technology.

[0115] 7 is a chart illustrating the performance of a high-pressure steam generating heat pump system compared to various conventional technologies, according to some embodiments. In some embodiments, the heat pump system 104 of the disclosed systems, methods, and apparatuses was used to generate high-pressure steam 140 compared to conventional high-temperature industrial heat pump technology. The heat pump system 104 outperformed the conventional high-temperature industrial heat pump.

[0116] In some embodiments, the primary competitive advantage of the disclosed systems, methods, and apparatus over conventional high temperature industrial heat pump technology has been the ability to produce steam at higher pressures, the ability to produce high pressure steam with a higher coefficient of performance, the ability to use a more advantageous refrigerant such as water, or a combination thereof.

[0117] In some embodiments, conventional high-temperature industrial heat pump technology using one or more hydrofluorocarbon (HFC) refrigerants and / or one or more hydrofluoroolefin (HFO) refrigerants produced thermal energy at temperatures up to 320°F (160°C). In some embodiments, conventional high-temperature industrial heat pumps cannot directly produce steam and must be used in conjunction with a non-combustion steam generator, which reduces the nominal temperature by 20°F. As a result, conventional high-temperature industrial heat pumps can produce a maximum saturated steam pressure of 3.5 barg (50 psi), which is insufficient to accommodate the medium-pressure applications (e.g., 3.5 barg to 20 barg) often required by industrial facilities 102. Furthermore, conventional industrial heat pumps have a relatively low coefficient of performance of less than 3.0, resulting in high power demands and high operating costs.

[0118] Furthermore, one or more HFC refrigerants have a high global warming potential (GWP). In contrast, one or more HFO refrigerants have a low GWP but are cost prohibitive. In contrast, the heat pump system 104 of the disclosed system, method, and apparatus directly generated high-pressure steam 140 at pressures up to 20 Barg (290 PSIg). Furthermore, the heat pump system 104 of the disclosed system, method, and apparatus generated high-pressure steam 140 at a COP 50% higher than a conventional high-temperature industrial heat pump when operated under the same operating conditions. As a result, the electrical demand and operating costs of the heat pump system 104 of the disclosed system, method, and apparatus were correspondingly reduced. Furthermore, the heat pump system 104 of the disclosed system, method, and apparatus used water as a refrigerant, offering the advantages of low cost, safety, non-toxicity, zero GWP, or a combination thereof.

[0119] Additionally, conventional CO2-based high-temperature industrial heat pumps have used a low-cost, low-GWP form of CO2 as a refrigerant. However, conventional high-temperature industrial CO2 heat pumps have been limited to temperatures below 238°F (114°C) due to the high pressure required for the refrigerant. Thus, as will be appreciated by those skilled in the art, although 238°F (114°C) is above the boiling point of water at atmospheric pressure, conventional high-temperature industrial CO2 heat pumps have been unable to generate sufficient high-pressure steam due to the need for a low reflux temperature below 203°F (95°C), a requirement that directly limits their ability to drive a steam generator.

[0120] Furthermore, conventional ammonia-based high-temperature industrial heat pumps were not suitable for steam generation due to their high-pressure characteristics that limited their maximum output temperature to 203°F (95°C).

[0121] 7, in some embodiments, the heat pump system 104 of the disclosed systems, methods, and apparatuses was used to generate high pressure steam 140 as opposed to conventional boiler technology, such as conventional electric boiler technology and / or conventional natural gas boiler technology. The heat pump system 104 performed better than the conventional boilers.

[0122] In some embodiments, a primary competitive advantage of the disclosed systems, methods, and apparatus over conventional electric boiler technology is the higher COP achieved by the disclosed systems, methods, and apparatus, resulting in lower operating costs. Furthermore, it was determined that conventional electric boiler technology, with a COP approaching 1.0, required approximately 295 kilowatt-hours (kWh) of electricity to produce 1 klb of steam. Assuming an industrial electricity price of $0.12 per kWh, each klb of steam produced by the conventional electric boiler technology required an energy cost of $35.40.

[0123] In contrast, the COP of the disclosed system, method, and apparatus was dependent on the temperature of the hot water source 110 received by the system 104, the temperature of the cooling water source 120 associated with the system 104, and common operating conditions of supplying 85°F hot water from the facility and generating 10 Barg (130 PSIg) high-pressure steam 140. Nevertheless, the COP of the disclosed system, method, and apparatus was 3.0 under these operating conditions. Furthermore, the disclosed system, method, and apparatus required only one-third the power of a conventional electric boiler, which required 97 kWh of power per klb of high-pressure steam. Furthermore, the disclosed system, method, and apparatus had an energy cost one-third the cost of a conventional electric boiler, i.e., $11.80 per klb of high-pressure steam.

[0124] Furthermore, the operating costs of the disclosed systems, methods, and apparatus were comparable to or lower than conventional natural gas boiler technology. For example, new conventional natural gas boiler technology using an economizer had a COP of 0.85 and required approximately 11.8 therms (thm) of natural gas to produce klb of high-pressure steam. At a natural gas price of $1.30 per thm, conventional natural gas boiler technology required an energy cost of $15.34 per klb of steam, which is greater than the $11.80 / klb cost achieved by the disclosed systems, methods, and apparatus.

[0125] 8 is a flowchart of an exemplary method (e.g., method 800) for generating high-pressure steam according to some embodiments, where dashed boxes represent optional elements in the flowchart. Specifically, method 800 is used to generate high-pressure steam (e.g., high-pressure steam 140-1 or 140-2 in FIG. 1A, high-pressure steam 140 in any of FIGS. 1-7, etc.). Various modules within memory 992 of computer system 900 perform specific steps of method 200 described in FIG. 2 unless expressly specified otherwise. Furthermore, it should be understood that the steps of FIG. 8 can be encoded in a single module or any combination of multiple modules.

[0126] In some embodiments, method 800 is implemented by heat pump system 104 of FIGS. 1-7. In some embodiments, method 800 is implemented in or in conjunction with a computer system (e.g., computer system 900 of FIG. 9, etc.). Computer system 900 includes one or more processors (e.g., CPU 972 of FIG. 9) and memory (e.g., memory 992 of FIG. 9) coupled to one or more processors 172. Memory 992 includes one or more programs (e.g., control module 906 of FIG. 9, client application 918 of FIG. 9, etc.) configured to execute on one or more processors 972. In other words, in some embodiments, method 800 cannot be performed intelligently because the computational complexity involved in resolving method 800 requires the use of computer system 900.

[0127] Referring to block 804 of FIG. 8, method 800 includes coupling a heat pump system (e.g., system 104 of any of FIGS. 1A-7) to one or more facilities (e.g., first facility 102-1 of FIG. 1A, second facility 102-2 of FIG. 1A, etc.). In some cases, the heat pump system may be connected to more than one facility. In some embodiments, each facility 102 is associated with an industrial process, such as a chemical process, a pulping process, a papermaking process, a metallurgical process, a refining process, a wood drying process, a packaging process, or a combination thereof. Those skilled in the art will appreciate that other industrial processes may be within the scope of the facility 102 of the present disclosure. Thus, method 800 enables the heat pump system 104 to be connected to one or more facilities 102 to provide the energy needs of the one or more facilities 102.

[0128] In some embodiments, the heat pump system 104 is connected to a hot water source (such as the hot water source 110 of any of FIGS. 1, 5, and 6). In some embodiments, the hot water source 110 is configured to capture waste heat from the first facility 102-1, thereby allowing the heat pump system 104 to utilize this waste heat through a heat transfer process. As a non-limiting example, in some embodiments, the hot water source 110 includes a high-temperature boiler feedwater (e.g., the boiler feedwater 160 of FIG. 1A) that has excess heat that is captured by the system 104. For example, in some embodiments, the hot water source 110 includes a cooling water return stream resulting from a cooling process performed at the facility 102 and / or a makeup water stream generated at the facility 102. In some embodiments, the cooling water return stream resulting from a cooling process performed at the facility 102 and / or the makeup water stream generated at the facility 102 are combined before being received by the system 104. However, the present disclosure is not limited in this respect. In some embodiments, additional hot water (e.g., boiler feedwater) is received by the system 104, for example, to maintain a constant water volume within the system 104. However, the disclosure is not limited in this respect. Accordingly, the hot water source 110 provides a low-grade heat source for the hot water received by the system 104. This heat source has energy in the form of heat that would normally be rejected from the facility 102 (e.g., to the atmosphere via a cooling tower process and / or to wastewater). Also, in some embodiments, the heat pump system 104 is further connected to an existing steam header in the same facility 102 (e.g., the first facility 102-1 in FIG. 1A ) or another facility 102 (e.g., the second facility 102-2 in FIG. 1A ). This allows the heat pump system 104 to have a one-to-one relationship with the facility 102 or a one-to-many relationship with two or more facilities 102. For example, in some embodiments, the heat pump system 104 is connected between a hot water source 110 configured to capture waste heat from the first facility 102-1 and an existing steam header at the first facility 102-1, thereby enabling the heat pump system 104 to generate high-pressure steam 140 that is subsequently utilized by the first facility 102-1.The high-pressure steam 140 is received from the hot water source 110 that captures waste heat from the first facility 102-1. As another non-limiting example, in some embodiments, the heat pump system 104 is connected between the hot water source 110 configured to capture waste heat from the first facility 102-1 and an existing steam header at the second facility 102-2. This allows the heat pump system 104 to generate high-pressure steam 140 that is subsequently utilized by the second facility 102-2. The high-pressure steam 140 is received from the hot water source 110 that captures waste heat from the first facility 102-1. Thus, by connecting the heat pump system 104 between the hot water source 110 of the facility 102-1 and an existing steam header at the same or another facility 102, the method 800 can optimize the efficiency of the heat pump system 104 without modifying or substantially modifying existing structures, such as the existing steam header at the same or another facility 102 connected to the heat pump system 104. In this manner, the heat pump system 104 allows for standardization of connections between the hot water source 110 of the facility 102 and an existing steam header of the same or another facility 102 .

[0129] Additionally, in some embodiments, the heat pump system 104 is connected to a steam condensate (e.g., steam condensate 214 in any of FIGS. 2-5 ). For example, in some embodiments, the heat pump system 104 is connected to a steam condensate 214 configured to receive waste condensate from an existing steam header in the first facility 102-1. This allows the heat pump system 104 to generate high-pressure steam 140 by recycling the steam condensate 214 that would otherwise be discharged from the first facility 102-1. In some embodiments, the heat pump system 104 is connected to a steam condensate 214 configured to receive waste condensate from a second facility 102-2 that is different from the first facility 102-1. However, the present disclosure is not limited in this respect.

[0130] In some embodiments, connecting the heat pump system 104 between the hot water source 110 of the facility 102 and an existing steam header of the same or another facility 102 further connects the heat pump system 104 to one or more utilities of the facility 102. For example, and referring briefly to FIG. 9 , in some embodiments, the heat pump system 104 is further connected to a power source of the facility 102 (e.g., power source 986 of FIG. 9 ) to deliver electricity (electricity 150 of FIG. 1B ) for use by the heat pump system 104, e.g., to drive one or more motors of a compressor train of the heat pump system 104 (e.g., compressor train 202 of any of FIGS. 2-5 ), thereby enabling electrical communication between the facility 102 and the heat pump system 104.

[0131] It should be noted that in various embodiments of the present application, "connect" broadly means "connect directly" or "connect indirectly" through additional structure.

[0132] 8, block 806, the method 800 includes receiving hot water from the hot water source 110 at the heat pump system 104. In some embodiments, the heat pump system 104 is configured to receive hot water at a first temperature from the hot water source 110. In some embodiments, the first temperature of the hot water received at the heat pump system 104 is between 60°F (15.6°C) and 150°F (65.6°C). In some embodiments, the first temperature of the hot water received at the heat pump system 104 is between 60°F (15.6°C) and 220°F (104°C). For example, in some embodiments, the heat pump system 104 may provide hot water from the hot water source 110 at temperatures ranging from 60°F (15.6°C) to 220°F (65.6°C), 60°F (15.6°C) to 205°F (96.1°C), 60°F (15.6°C) to 190°F (87.8°C), 60°F (15.6°C) to 175°F (79.4°C), 60°F (15.6°C) to 150°F (65.6°C), 60°F (15.6°C) to 180°F (185°C), 60°F (15.6°C) to 190°F (87.8°C), 60°F (15.6°C) to 175°F (79.4°C), 60°F (15.6°C) to 150°F (65.6°C), 60°F (15.6°C) to 185°F (185°C), 60°F (15.6°C) to 190°F (87.8 ... °C)~135°F(57.2°C), 60°F(15.6°C)~120°F(48.9°C), 60°F(15.6°C)~105°F(40.6°C), 60°F(15.6°C)~90°F(32 .2°C), 60°F(15.6°C)~75°F(23.9°F), 80°F(26.7°C)~220°F(65.6°C), 80°F(26.7°C)~205°F(96.1°C), 80°F(2 6.7°C)~190°F(87.8°C), 80°F(26.7°C)~175°F(79.4°C), 80°F(26.7°C)~150°F(65.6°C), 80°F(26.7°C)~135° F(57.2°C), 80°F(26.7°C)~120°F(48.9°C), 80°F(26.7°C)~105°F(40.6°C), 80°F(26.7°C)~90°F(32.2°C), 10 0°F(37.8°C)~220°F(65.6°C), 100°F(37.8°C)~205°F(96.1°C), 100°F(37.8°C)~190°F(87.8°C), 100°F(37.8 °C)~190°F(87.8°C), (37.8°C)~175°F(79.4°C), 100°F(37.8°C)~150°F(65.6°C), 100°F(37.8°C)~135°F(57.2°C), 100°F (37.8°C) ~ 120°F (48.9°C), 100°F (37.8°C) ~ 105°F (40.6°C), 120°F (48.9 °C)~220°F(65.6°C), 120°F(48.9°C)~205°F(96.1°C), 120°F(48.9°C)~190°F(87.8° C), 120°F (48.9°C) ~ 175°F (79.4°C), 120°F (48.9°C) ~ 150°F (65.6°C), 120°F (48.9°C) )~135°F(57.2°C), 140°F(60.0°C)~220°F(65.6°C), 140°F(60.0°C)~205°F(96.1°C) , 140°F (60.0°C) ~ 190°F (87.8°C), 140°F (60.0°C) ~ 175°F (79.4°C), 140°F (60.0°C) ~ 150°F (65.6°C), 175°F (79.4°C) ~ 220°F (65.6°C), 175°F (79.4°C) ~ 205°F (96.1°C), 1 The device is configured to receive hot water at a first temperature of 75°F (79.4°C) to 190°F (87.8°C), 190°F (87.8°C) to 220°F (65.6°C), 190°F (87.8°C) to 205°F (96.1°C), or 205°F (96.1°C) to 220°F (65.6°C), inclusive. In some embodiments, the first temperature of the hot water from the hot water source 110 received by the heat pump system 104 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 (38.8°C), at least 110°F (39.8°C), at least 120°F (39.8°C), at least 130°F (39.8°C), at least 140°F (39.8°C), at least 150°F (39.8°C), at least 160°F (39.8°C), at least 170°F (39.8°C), at least 180°F (39.8°C), at least 190°F (39.8°C), at least 200°F (20.8°C), at least 210°F (21.8°C), at least 220°F (22.8°C), at least 230°F (23.8°C), at least 240°F (24.8°C), at least 250°F (25.8°C), at least 260°F (26.8°C), at least 270°F (27.8°C), at least 280°F (28.8°C), at least 290°F (30.8°C), at least 300°F (30.8°C), at least 310°F (3 °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 of the hot water received by the heat pump system 104 from the hot water source 110 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 (100°C), at most 105°F (110°C), at most 115°F (120°C), at most 125°F (130°C), at most 130°F (140°C), at most 145°F (150°C), at most 150°F (160°C), at most 165°F (170°C), at most 175°F (180°C), at most 180°F (180°C), at most 190°F (200°C), at most 210°F (210°C), at most 220°F (220°C), at most 230°F (230°C), at most 240°F (240°C), at most 250°F (250°C), at most 260°F (260°C), at most 270°F (270°C), at most 280°F (280°C), at most 290°F (290°C), at most 300°F (300°C), at most 310°F (310°C), at most 320°F (320°C), at most 330°F (330°C), at most 340°F (340°C), at most 350°F (350°C), at F (32.2°C), Highest 95°F (35.0°C), Highest 100°F (37.8°C), 105°F (40.6°C), Highest 110°F (43.3°C), Highest 115°F (46.1°C), Highest 120°F (48.9°C), Highest 125°F (51.7°C), Highest 130°F (54.4°C), Highest 135°F (57.2°C), Highest 140°F (60.0°C), Highest 145°F (62.8°C), Highest 150°F (65.6°C), Highest 155°F (68.3°C), Highest 160°F (71.1°C), Highest 165°F (73.9°C), Highest 170°F (76.7°C), Highest 175°F (79.4°C), Highest 18 0°F (82.2°C), up to 185°F (85.0°C), up to 190°F (87.8°C), up to 195°F (90.6°C), up to 200°F (93.3°C), up to 205°F (96.1°C), up to 210°F (98.9°C), up to 215°F (102°C), or up to 220°F (104°C). For example, in some embodiments, hot water source 110 is used to receive low-grade heat as hot water. This low-grade heat is supplied from existing, commonly available on-site heat sources, such as cooling water return in a cooling tower process, and is typically between 85°F (29.4°C) and 90°F (32.2°C). In some embodiments, low-grade heat in the form of hot water is provided from dryer exhaust air at a temperature between 140°F (60.0°C) and 180°F (82.2°C). In some embodiments, system 104 includes a heat exchange mechanism interposed between hot water source 110 and the inlet of system 104. This heat exchange mechanism allows the heat of the hot water to be transferred to the heat pump water loop of system 104. For example, in some embodiments, the heat exchange mechanism is configured to generate condensate (e.g., condensate 180 in FIG. 1A) in either facility 102 or system 104. However, the present disclosure is not limited in this respect.

[0133] In some embodiments, the system 104 further includes a water loop, such as a closed water loop. In some embodiments, the water loop includes an upstream portion and a downstream portion. In some embodiments, the downstream portion is configured to receive heated water from the same or another facility. In some embodiments, the upstream portion is configured to supply chilled water to the same or another facility. Also, in some embodiments, the water loop is heated by the same or another facility.

[0134] Referring to block 808 of FIG. 8, method 800 includes passing hot water through heat pump system 104 to generate high-pressure steam (e.g., high-pressure steam of method 800 of FIG. 8, high-pressure steam 140-1 or 140-2 of FIG. 1B, high-pressure steam 140 of any of FIGS. 1A-7, etc.).

[0135] For example, in some embodiments, the heat pump system 104 includes a compressor train (e.g., compressor train 202 of any of Figures 2-5) and a flash vessel train (e.g., flash vessel 212 of any of Figures 2A-5B), both of which are used in conjunction with method 800 to generate high-pressure steam 140 for the facility 102.

[0136] More specifically, in some embodiments, passing hot water through the heat pump system 104 to generate high-pressure steam 140 includes expanding the hot water in a flash vessel (e.g., the first flash vessel 212-1 in any of FIGS. 2-5 ). The flash vessel 212 expands the hot water to generate low-pressure steam 206, which is then used by the compressor train 202. Also, in some such embodiments, because the hot water is expanded in the flash vessel 212, the low-pressure steam 206 generated in the flash vessel has a lower temperature than the hot water received by the heat pump system 104. In other words, in some such embodiments, the second temperature of the first low-pressure steam 206 generated in the first flash vessel 212-1 is lower than the first temperature of the hot water source 110. Also, in some such embodiments, the flash vessel 212 operates in a passive steady-state when generating the low-pressure steam 206, thereby increasing the efficiency of the heat pump system 104. However, the present disclosure is not limited in this respect.

[0137] In some embodiments, the method 800 may be used to measure pressures between 0.256 pounds per square inch (PSI) (17.7 millibar (mBar)) and 3.72 PSI (257 mBar), between 0.256 PSI (17.7 mBar) and 3.2 PSI (221 mBar), between 0.256 PSI (17.7 mBar) and 2.7 PSI (186 mBar), between 0.256 PSI (17.7 mBar) and 1.2 PSI (82.7 mBar), between 0.256 PSI (17.7 mBar) and 0.7 PSI (48.3 mBar), between 0.35 PSI (24.1 mBar) and 3.72 PSI (257 mBar). ar), 0.35PSI(24.1mBar)~3.72PSI(257mBar), 0.35PSI(24.1mBar)~3.72PSI(257mBar), 0.PSI(24.1mBar)~3.2PSI(221mBar), 0.35PSI(24.1mBar) ~2.7PSI(186mBar), 0.35PSI(24.1mBar)~1.2PSI(82.7mBar), 0.35PSI(24.1mBar)~0.7PSI(48.3mBar), 0.85PSI(58.6mBar)~3.72PSI(257mBar), 0 .85PSI(58.6mBar)~3.2PSI(221mBar), 0.85PSI(58.6mBar)~2.7PSI(186mBar), 0.85PSI(58.6mBar)~1.2PSI(82.7mBar), 1.35PSI(93.1mBar)~3.7 2PSI(257mBar), 1.35PSI(93.1mBar)~3.2PSI(221mBar), 1.35PSI(93.1mBar)~2.7PSI(186mBar), 1.85PSI(128mBar)~3.72PSI(257mBar), 1.85PSI (128mBar)~3.2PSI(221mBar), 1.85PSI(128mBar)~2.7PSI(186mBar), 2.35PSI(162mBar)~3.72PSI(257mBar), 2.35PSI(162mBar)~3.2PSI(221mBar) r), 2.35PSI(162mBar)~2.7PSI(186mBar), 2.85PSI(197mBar)~3.72PSI(257mBar), 2.85PSI(197mBar)~3.2PSI(221mBar), or 3.35PSI(231mBar)~3.The first low pressure steam 206-1 is generated at a first pressure of 72 PSI (257 mBar), inclusive. In some embodiments, the first pressure is at least 0.256 PSI (17.7 mBar), at least 0.363 PSI (25 mBar), at least 0.35 PSI (24.1 mBar), at least 0.5 PSI (34.5 mBar), at least 0.7 PSI (48.3 mBar), at least 0.85 PSI (58.6 mBar), at least 1 PSI (68.9 mBar), at least 1.2 PSI (82.7 mBar), at least 1.3 PSI (89.6 mBar), at least 1.35 PSI (93.1 mBar), at least 1.5 PSI (103 mBar), at least 1.6 5 PSI (114 mBar), at least 1.85 PSI (128 mBar), at least 2 PSI (138 mBar), at least 2.2 PSI (152 mBar), at least 2.35 PSI (162 mBar), at least 2.5 PSI (172 mBar), at least 2.7 PSI (186 mBar), at least 2.85 PSI (197 mBar), at least 3 PSI (207 mBar), at least 3.2 PSI (221 mBar), at least 3.35 PSI (231 mBar), at least 3.5 PSI (241 mBar), or at least 3.72 PSI (257 mBar). In some embodiments, the first pressure is at most 0.256 PSI (17.7 mBar), at most 0.363 PSI (25 mBar), at most 0.35 PSI (24.1 mBar), at most 0.5 PSI (34.5 mBar), at most 0.7 PSI (48.3 mBar), at most 0.85 PSI (58.6 mBar), at most 1 PSI (68.9 mBar), at most 1.2 PSI (82.7 mBar), at most 1.3 PSI (89.6mBar), Max 1.35PSI (93.1mBar), Max 1.5PSI (103mBar), Max 1.65PSI (114mBar), Max 1.85PSI (128mBar), Max 2PSI (138mBar), Max 2.2PSI (152mBar), Max 2.35PSI (162mBar), Max 2.5PSI (172mBar), Max 2.7PSI (186mBar), Max 2.85 PSI (197 mBar), maximum 3 PSI (207 mBar), maximum 3.2 PSI (221 mBar), maximum 3.35 PSI (231 mBar), maximum 3.5 PSI (241 mBar), or maximum 3.72 PSI (257 mBar).

[0138] In some embodiments, expanding the hot water in the flash vessel 212 as it passes through the heat pump system 104 further produces cooling water (e.g., condensate) from the hot water. In some embodiments, the cooling water produced in the flash vessel 212 has a lower temperature than the hot water. In other words, in some such embodiments, the third temperature of the cooling water produced in the flash vessel 212 is lower than the first temperature of the hot water source 110. Also, in some embodiments, the third temperature of the cooling water is lower than the second temperature of the low-pressure steam 206 produced in the flash vessel 212. Thus, by expanding the hot water in the flash vessel 212, the heat pump system 104 increases the thermal energy of a portion of the hot water from the hot water source 110 by forming low-pressure steam 206 derived from the cooling water produced in the flash vessel 212. For example, in some embodiments, the facility 102 is configured to utilize the high-pressure steam 140 produced in the system 104, which produces a cooling water source 120 at a third temperature lower than the first temperature of the hot water from the hot water source 31-0. However, the present disclosure is not limited to this.

[0139] Further, in some embodiments, the pressure in the flash vessel 212 is less than the saturation pressure of the hot water. For example, in some embodiments, passing the hot water through the heat pump system 104 further includes compressing the low-pressure steam 206 into a first high-pressure steam having a higher pressure. For example, briefly referring to FIG. 2A , in some embodiments, the first low-pressure steam 206 having a first pressure is further compressed by a second compressor 204-2, which generates a first high-pressure steam having a higher pressure than the first low-pressure steam, such as second low-pressure steam 206-2 generated by the second compressor 204-2, which has a higher pressure than the first low-pressure steam 206-1 generated by the first compressor 204-1. Thus, in some such embodiments, the first high-pressure steam, which has a higher pressure than the first low-pressure steam, includes low-pressure steam 206 generated in one or more compressors 204 downstream from the first compressor 204-1 that generated the first low-pressure steam 206-1. However, the present disclosure is not limited in this respect. For example, in some embodiments, the first high-pressure steam, which has a higher pressure than the first low-pressure steam, includes high-pressure steam 140 generated by the heat pump system 104 for use by the facility 102.

[0140] In some embodiments, passing the hot water through the heat pump system 104 further includes introducing the hot water into the first high-pressure steam (e.g., the first low-pressure steam 206-1 produced in the first flash vessel 212-1 of any of FIGS. 2-5, the second low-pressure steam 206-2 produced in the second flash vessel 212-2 of any of FIGS. 2-5, ..., the low-pressure steam 206-n produced in the nth flash vessel 212-n, etc.). In some embodiments, the hot water is introduced into the first high-pressure steam to reduce the temperature of the first high-pressure steam to saturated first high-pressure steam.

[0141] In some embodiments, passing the hot water through the heat pump system 104 further includes repeating the compression and introduction steps a desired number of times to produce high pressure steam.

[0142] In some embodiments, the desired number is greater than 1. In some embodiments, the desired number is greater than 1 but less than 21. In some embodiments, the desired number of times is 2 to 20 times, 2 to 17 times, 2 to 15 times, 2 to 12 times, 2 to 9 times, 2 to 6 times, 2 to 3 times, 3 to 20 times, 3 to 17 times, 3 to 15 times, 3 to 12 times, 3 to 9 times, 3 to 6 times, 5 to 20 times, 5 to 17 times, 5 to 15 times, 5 to 12 times, 5 to 9 times, 5 to 6 times, 7 to 20 times, 7 to 17 times, 7 to 15 times, 7 to 12 times, 7 to 9 times, 9 to 20 times, 9 to 17 times, 9 to 15 times, 9 to 12 times, 11 to 20 times, 11 to 17 times, 11 to 15 times, 11 to 12 times, 13 to 20 times, 13 to 17 times, 13 to 15 times, 15 to 20 times, 15 to 17 times, or 17 to 20 times (inclusive). In some embodiments, the desired number of times is at least 2, at least 3, at least 4, at least 5, at least 6, at least 7, at least 8, at least 9, at least 10, at least 11, at least 12, at least 13, at least 14, at least 15, at least 16, at least 17, at least 18, at least 19, or at least 20. In some embodiments, the desired number of times is at most 2, at most 3, at most 4, at most 5, at most 6, at most 7, at most 8, at most 9, at most 10, at most 11, at most 12, at most 13, at most 14, at most 15, at most 16, at most 17, at most 18, at most 19, or at most 20.

[0143] Referring to block 810 of FIG. 8 , in some embodiments, the method 800 includes supplying high-pressure steam 140 from the heat pump system 104 to an existing steam header in the same or another facility 102 that supplies hot water to the heat pump system 104.

[0144] In some embodiments, the high pressure steam 140 is between 10 kilopounds per hour (klb / hr) and 300 klb / hr, between 10 klb / hr and 250 klb / hr, between 10 klb / hr and 200 klb / hr, between 10 klb / hr and 150 klb / hr, between 10 klb / hr and 100 klb / hr, between 10 klb / hr and 50 klb / hr, between 75 klb / hr and 300 klb / hr, between 75 klb / hr and 250 klb / hr, between 75 klb / hr and 20 The heat pump system 104 supplies the same or another facility 102 with a mass flow rate of 0 klb / hr, 75 klb / hr to 150 klb / hr, 75 klb / hr to 100 klb / hr, 150 klb / hr to 300 klb / hr, 150 klb / hr to 250 klb / hr, 150 klb / hr to 200 klb / hr, 225 klb / hr to 300 klb / hr, or 225 klb / hr to 250 klb / hr (inclusive). In some embodiments, the mass flow rate of the high pressure steam generated by the heat pump system 104 is at least 10 klb / hr, at least 25 klb / hr, at least 50 klb / hr, at least 75 klb / hr, at least 100 klb / hr, at least 125 klb / hr, at least 150 klb / hr, at least 175 klb / hr, at least 200 klb / hr, at least 225 klb / hr, at least 250 klb / hr, at least 275 klb / hr, or at least 300 klb / hr. In some embodiments, the mass flow rate of the high pressure steam generated by the heat pump system 104 is at most 10 klb / hr, at most 25 klb / hr, at most 50 klb / hr, at most 75 klb / hr, at most 100 klb / hr, at most 125 klb / hr, at most 150 klb / hr, at most 175 klb / hr, at most 200 klb / hr, at most 225 klb / hr, at most 250 klb / hr, at most 275 klb / hr, or at most 300 klb / hr.

[0145] In this disclosure, descriptions of devices and systems include one or more computer implementations unless explicitly stated otherwise. For example, for illustrative purposes, computer system 900 in FIG. 9 is depicted as a single device containing all of the functionality of computer system 900. However, the present disclosure is not limited thereto. For example, in some embodiments, the functionality of computer system 900 may be distributed across any number of networked computers and / or may reside on each of several networked computers and / or by being hosted on one or more virtual machines and / or containers at remote locations accessible via a communications network (e.g., communications network 984). Those skilled in the art will appreciate that a wide range of different computer topologies are possible for computer system 900 and other devices and systems of the present disclosure, and all such topologies are within the scope of the present disclosure. Also, rather than relying on a physical communications network 984, the illustrated devices and systems may transmit information to each other wirelessly. Thus, the exemplary topology depicted in FIG. 9 is merely useful for illustrating features of some embodiments of the present disclosure, as will be readily understood by those skilled in the art.

[0146] 9 is a block diagram illustrating an exemplary computer system 900 applied to a high-pressure steam generating heat pump system, according to some embodiments. The computer system 900 is configured to control the generation of high-pressure steam in a heat pump system (e.g., the heat pump system 104 of FIGS. 1-7). In some embodiments, the computer system 900 is associated with a facility (e.g., the first facility 102-1 of FIG. 3, the heat pump system 104 of any of FIGS. 1A-7, the second facility 102-2 of FIG. 1A, etc.). 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.

[0147] In some embodiments, communications 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 communications network 984 include the World Wide Web (WWW), intranets, and / or wireless networks such as cellular networks, wireless local area networks (LANs) and / or metropolitan area networks (MANs), and other devices via wireless communications. Wireless communications may include 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-HSPA), 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 802.11a, IEEE 802.11ac, IEEE 802.11ax, IEEE 802.11b, IEEE 802.11g and / or IEEE 802.11a / b / g), and / or IEEE 802.11ac / b / g. Optionally, the communication may use any of a number of communications standards, protocols, and technologies, including IEEE 802.11n), Voice over Internet Protocol (VoIP), Wi-MAX, protocols for email (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 Enhancements (SIMPLE), Instant Messaging and Presence Service (IMPS)), and / or Short Message Service (SMS), or other suitable communications protocols (including communications protocols not yet developed as of the filing date of this document).

[0148] In various embodiments, computer system 900 includes one or more processing units (CPUs) 972 , a network or other communication interface 974 , and memory 992 .

[0149] In some embodiments, computer system 900 includes a user interface 976. User interface 976 typically includes a display 978 for presenting media such as the status of each device (e.g., first device 910-1, second device 910-2, ..., Qth device 912-Q in FIG. 9 ). In some embodiments, display 978 is integrated within the computer system (e.g., housed in the same chassis as CPU 972 and memory 992). In some embodiments, computer system 900 includes one or more input devices 980 that allow a subject to interact with computer system 900. In some embodiments, input device 980 includes a keyboard, a mouse, and / or other input mechanism. Alternatively, or additionally, in some embodiments, display 978 includes a touch-sensitive surface (e.g., if display 978 is a touch-sensitive display or computer system 900 includes a touchpad).

[0150] In some embodiments, computer system 900 presents media to a user via display 978. Examples of media presented by display 978 include one or more images, video, audio (e.g., waveforms of audio samples), or combinations thereof. In a typical embodiment, the one or more images, videos, audio, or combinations thereof are presented by display 978 via a client application stored in memory 992. In some embodiments, audio is presented via an external device (e.g., speakers, headphones, an input / output (I / O) subsystem, etc.) that receives audio information from computer system 900 and presents audio data based on the audio information. In some embodiments, user interface 976 also includes an audio output device, such as a speaker, or an audio output for connecting to speakers, earphones, or headphones.

[0151] Memory 992 includes high-speed random-access memory such as DRAM, SRAM, DDRRAM, 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. Memory 992 may optionally include one or more storage devices located remotely from CPU(s) 972. Memory 992, or alternatively, the non-volatile memory device(s) within memory 992, comprises a non-transitory computer-readable storage medium. Access to memory 992 by other components of computer system 900, such as CPU(s) 972, is optionally controlled by a controller. In some embodiments, memory 992 may include mass storage located remotely relative to CPU(s) 972. In other words, some data stored in memory 992 may actually be hosted on a device external to computer system 900 but accessible electronically by computer system 900 via the Internet, an intranet, or other form of network 984 or electronic cable using communication interface 974.

[0152] In some embodiments, the memory 992 of the computer system 900 for generating high pressure steam stores: An operating system 902 (e.g., an embedded operating system such as ANDROID, iOS, DARWIN, RTXC, LINUX, UNIX, OSX, WINDOWS, or VxWorks) that includes procedures for handling various basic system services; · optionally, an electronic address 904 associated with the computer system 900 that identifies the computer system 900 (e.g., within the communications network 984, within the facility network, etc.); a control module 906 facilitating control of one or more operations performed in generating high-pressure steam in response to a plurality of heuristic instructions, the control module 906 including an equipment module 908 that stores records of a plurality of equipment 910 (e.g., first equipment 910-1, second equipment 910-2, ..., equipment 910-Q of FIG. 9 ) for generating high-pressure steam, and further including a task module 912 that stores a plurality of tasks 914, each task 914 defining an operation for generating high-pressure steam in the heat pump system in response to one or more parameters 916 associated with the respective task 914; · Optionally, a client application 918 for presenting information (e.g., media) such as the status of steps and / or processes of the method for generating high pressure steam (e.g., method 800 of FIG. 8 ) using a display 978 of the computer system 900.

[0153] As described above, an optional electronic address 904 is associated with computer system 900. The optional electronic address 904 is used to at least uniquely identify computer system 900 from other devices and components of distributed system 900, such as other devices with access to communication network 984 (e.g., facility 102). For example, in some embodiments, electronic address 904 is used to receive a request from a remote device associated with first facility 102-1 to initiate, using computer system 900, the generation of high-pressure steam to be used for second facility 102-2. However, the present disclosure is not limited in this respect. In some embodiments, electronic address 904 is used to receive a request from a remote device associated with first facility 102-1 to initiate, using computer system 900, the generation of high-pressure steam to be used for first facility 102-1.

[0154] In some embodiments, the computer system 900 includes a control module 906 (hereinafter referred to as a "controller") configured to control one or more operations performed in generating high-pressure steam. Specifically, the controller 906 is configured to control one or more operations performed in generating high-pressure steam in response to a plurality of heuristic instructions. By way of non-limiting example, in some embodiments, the plurality of heuristic instructions include one or more proportional-integral-derivative (PID) loop instructions and / or one or more variable frequency drive (VFD) instructions. For example, in some embodiments, the controller 906 is in electronic communication with one or more sensors (e.g., sensor 982 in FIG. 9 ), each of which is configured to determine a condition associated with a respective piece of equipment 910.In some embodiments, the controller 906 is in electronic communication with one or more sensors 982, the one or more sensors 982 being configured to determine one or more temperatures associated with a system (e.g., the heat pump system of method 800 of FIG. 8 , system 104 of any of FIGS. 1-7 , etc.) (e.g., the temperature of hot water received by system 104, the temperature of low-pressure steam generated by a flash vessel train of system 104, the temperature of high-pressure steam generated by a compressor train of system 104, the temperature of a steam condensate source received by system 104, the temperature of condensate generated by system 104, temperature losses in some or all of system 104, etc.), a first set of sensors 982 configured to determine one or more pressures associated with system 104 (e.g., the internal pressure of a flash vessel train, the pressure ratio of a compressor train, the pressure losses in some or all of system 104, etc.), a second set of sensors 982 configured to determine one or more pressures associated with system 104 (e.g., the internal pressure of a flash vessel train, the pressure ratio of a compressor train, the pressure losses in some or all of system 104, etc.), a pressure ratio of a pressure ... a third set of sensors 982 configured to determine one or more flow rates associated with the system 104 (e.g., the mass flow rate of hot water received by the system 104, the mass flow rate of low-pressure steam generated by the flash vessel train of the system 104, the mass flow rate of high-pressure steam generated by the compressor train of the system 104, etc.); a fourth set of sensors 982 configured to determine one or more rates associated with the system 104 (e.g., the rate of hot water received by the system 104, the rate of low-pressure steam generated by the flash vessel train 210 of the system 104, the rate of high-pressure steam generated by the compressor train 202 of the system, the rate of a steam condensate source received by the system 104, etc.); a fifth set of sensors 982 configured to determine one or more electrical conditions 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 arcing, one or more grounds, etc.), or any combination thereof. Thus, controller 906, in electronic communication with one or more sensors 982, enables computer system 900 to control the flow rate of high-pressure steam generated by system 104, which is received by facility 102. However, the present disclosure is not limited in this respect.

[0155] Equipment 910 is an apparatus, device, mechanism, or combination thereof that performs a particular function or functions in system 104 to generate high-pressure steam, such as a high-pressure steam product associated with system 104 (e.g., high-pressure steam in method 800 of FIG. 8, high-pressure steam 140-1 or 140-2 in FIG. 1A, high-pressure steam 140 in any of FIGS. 2A-7, etc.), or a cooling water product (e.g., cooling water source 120 in any of FIGS. 1A-6, etc.). For example, in some embodiments, each of plurality of equipment 910 is configured to perform a particular task 914 or tasks 914 in system 104 to generate high-pressure steam 140. Examples of equipment 910 include, but are not limited to, a blower, a boiler (e.g., a heat recovery boiler, such as boiler 236 in FIG. 5A), a burner, a compressor (e.g., first compressor 204-1 in compressor train 202 in FIG. 2), a conduit (e.g., a first conduit carrying hot water received at hot water source 110 in FIG. 2, a second conduit carrying low-pressure steam 206 generated in flash vessel 212, etc.), an attemperator (e.g., first attemperator 232-1 in attemperator train 230 in FIG. 5A), a drum, a heat exchanger, a pump (e.g., repressurization pump 220 in FIG. 5A), a pipe, a reservoir, a valve (e.g., valve 218-1 in FIG. 3), a vessel (e.g., a flash vessel), etc. For example, in some embodiments, the one or more pieces of equipment 910 include a compressor train 202 that further includes a series of at least two compressors 204 configured to supply high-pressure steam 140 to an existing steam header (e.g., block 810 in FIG. 8 ) at a facility (e.g., facility 102-1 in FIG. 1A ). However, the present disclosure is not limited in this respect.

[0156] In some embodiments, each task 914 is associated with a function, step, or process (such as a function, step, or process of method 800 of FIG. 8 ) performed by a set of equipment 910 in generating high-pressure steam 140 . As non-limiting examples, in some embodiments, the one or more tasks 914 to generate high-pressure steam 940 include receiving hot water (e.g., block 806 in FIG. 8 ), determining a first temperature of the hot water received from the hot water source 110, determining a saturation pressure of the hot water received from the hot water source 110, passing the hot water through the system 104 (e.g., block 808 in FIG. 8 ), expanding the hot water in a flash vessel (e.g., block 808 in FIG. 8 ), generating low-pressure steam (e.g., block 808 in FIG. 2 ), generating cooling water (e.g., block 808 in FIG. 8 ), maintaining the flash vessel at a first pressure lower than the saturation pressure of the hot water (e.g., block 808 in FIG. 8 ), compressing the low-pressure steam (e.g., block 808 in FIG. 8 ), attenuating the low-pressure steam, supplying the high-pressure steam from the system 104 to an existing steam header in the facility 102 (e.g., block 810 in FIG. 8 ), etc.

[0157] Each task 914 also includes a set of parameters 916 that are used by the respective device 910 when performing its function. In some embodiments, each task 914 has a logical dependency on an operation that defines the function performed by the respective device 910. For example, in some embodiments, a task 914 is a first operation that a first device 910-1 performs using a first set of parameters 916, and a second task 914-2 is a second operation that a second device 910-2 performs using a first set of parameters 916. As non-limiting examples, in some embodiments, the parameters 916 may include a temperature of hot water supplied from the hot water source 110 to the system 104, a pressure of hot water supplied from the hot water source 110 to the system 104, a mass flow rate of hot water supplied from the hot water source 110 to the system 104, a temperature of low-pressure steam 206 generated by the system 104, a pressure of low-pressure steam 206 generated by the system 104, a mass flow rate of low-pressure steam 206 generated by the system 104, a temperature of high-pressure steam 140 ... These parameters may include the pressure of the high-pressure steam 140 generated by the system 104, the mass flow rate of the high-pressure steam 140 generated by the system 104, the temperature of the cooling water from the cooling water source 120 generated by the system 104, the pressure of the cooling water from the cooling water source 120 generated by the system 104, the mass flow rate of the cooling water from the cooling water source 120 generated by the system 104, the temperature of the steam condensate 214 received by the system 104, the pressure of the steam condensate 214 received by the system 104, the mass flow rate of the steam condensate 214 received by the system 104, etc. As a non-limiting example, in some embodiments, the computer system 900 sets one or more parameters 916, including a flow parameter 916 (e.g., mass flow rate), a pressure parameter 916, a temperature parameter 916, a direction parameter 916, etc., associated with each piece of equipment 910 to optimize the generation of high-pressure steam 140 in the system 104. However, the present disclosure is not limited thereto.

[0158] Each of the above-identified modules and applications corresponds to a set of executable instructions for performing one or more of the functions described above and methods described in this disclosure (e.g., computer-implemented methods and other information processing methods described herein, such as method 800 of FIG. 8). These modules (i.e., sets of instructions) need not be implemented as separate software programs, procedures, or modules; therefore, various subsets of these modules are optionally combined or otherwise reconfigured in various embodiments of the present disclosure. In some embodiments, memory 992 optionally stores a subset of the above-identified modules and data structures. Additionally, memory 992 stores additional modules and data structures not described above.

[0159] It should be understood that the computer system 900 of Figure 9 is merely one example of a computer system 900, and optionally has more or fewer components than those shown, optionally two or more components combined, or optionally a different configuration or arrangement of components. The various components shown in Figure 9 may be implemented in hardware, software, firmware, or a combination thereof, including one or more signal processing and / or application specific integrated circuits.

[0160] Additional exemplary implementations of the heat pump system 400 are described below. Example 1: A heat pump system of the present disclosure configured to modularly connect to a facility's existing steam header

[0161] In some embodiments, a heat pump system (e.g., heat pump system 104 of any of FIGS. 1A-7) was configured to have modular characteristics through a product family and / or facility (e.g., facility 102-1 of FIG. 1A, facility 102-2 of FIG. 1A, etc.) family approach. More specifically, in some embodiments, a baseline heat pump system 104 was configured to receive hot water at the lowest specified temperature in the family of facilities 102, generate high-pressure steam 140 at the highest specified pressure in the family of facilities 102, and deliver high-pressure steam at a maximum flow rate. In some embodiments, for a facility 102 with an elevated hot water temperature relative to other facilities in the family of facilities 102, the baseline heat pump system 104 was modified by reducing (e.g., removing) one or more compressors 204 located in a downstream (e.g., lower-pressure) portion of the compressor train 202 of the facility 102. In some embodiments, for facilities 102 in a family of facilities 102 with reduced outlet steam pressure, the baseline heat pump system 104 was modified by reducing (e.g., removing) one or more compressors 204 located upstream (e.g., on the high-pressure side) of the compressor train 202. In some embodiments, for facilities 102 in a family of facilities 102 with reduced flow rate of high-pressure steam 140, the baseline heat pump system 104 was modified by determining the first temperature of the hot water received from the facility 102 and the outlet pressure of the high-pressure steam received at the facility 102, and selecting an appropriate facility sized to allow the desired flow rate of high-pressure steam 140.

[0162] In some embodiments, one or more components of the system 104 are arranged on a modular skid or container designed for ease of shipping and final assembly.

[0163] In some embodiments, the reference heat pump system 104 was configured to address edges in operating parameters 916, such as a minimum hot water source 110 temperature, a minimum steam condensate 214 temperature, a maximum high-pressure steam 140 temperature, a maximum high-pressure steam 140 pressure, a maximum high-pressure steam 140 flow rate, or a combination thereof. In some embodiments, one or more portions of the compressor train 202 and / or flash vessel train 210 were removed from the reference heat pump system 104 to accommodate higher heat source temperatures and / or lower steam outlet temperatures and / or pressures. For example, in some embodiments, the reference heat pump system 104 was configured such that the minimum hot water source 110 temperature received from the facility 102 was at least 60 degrees Fahrenheit (°F) (15.6 degrees Celsius (°C)) or at least 80 degrees Fahrenheit (26.7°C).

[0164] In some embodiments, the baseline heat pump system 104 was modified by increasing the pressure of the flash vessel train 210 and decreasing the pressure of one or more compressors 204 located at the front end of the compressor train 202 in accordance with a determination that the temperature of the hot water source 110 was 80°F (26.7°C) or greater.

[0165] In some embodiments, the baseline heat pump system 104 was modified by reducing one or more compressors 204 located at the rear end of the compressor train 202 pursuant to a determination that the pressure of the high-pressure steam 140 received at the facility was less than 290 PSIg (20 Bar).

[0166] In some embodiments, following a determination that the required flow rate for high-pressure steam 140 is less than 50 kilopounds per hour (klb), one or more flash vessels 212 in flash vessel train 210 and / or one or more compressors 204 in compressor train 202 are replaced with one or more flash vessels 212 and / or one or more compressors 204 configured for a lower flow rate.

[0167] As pressure increases, the density of steam increases, and therefore the mass flow rate for a given size compressor 204 also increases. Thus, in some embodiments, the disclosed systems, methods, and apparatus utilized an upper limit for an operating parameter, such as 20 Barg output pressure of high-pressure steam 140, to determine the minimum flow rate (e.g., after attenuation by attenuator train 230) at which compressor train 202 would produce such pressure with high efficiency and maximum compression ratio. In some embodiments, the disclosed systems, methods, and apparatus determined the inlet pressure of hot water from hot water source 110 required to achieve a 20 Barg output pressure of the generated high-pressure steam at that minimum flow rate. In some embodiments, the disclosed systems, methods, and apparatus repeated this process for the remaining compressors 204 in compressor train 202 until the inlet pressure of the hot water received by system 104 reached 35 mBara.

[0168] In some embodiments, the baseline heat pump system 104 was modified in response to a set of specific parameter requirements related to the performance of the heat pump system 104 and / or one or more processes performed at the facility. For example, in some embodiments, the set of specific parameter 916 requirements included the temperature of the hot water source 110 received by the system 104, the pressure of the high-pressure steam 140 produced by the system 104, and the mass flow rate of the high-pressure steam 140 produced by the system 104. In some embodiments, the disclosed systems, methods, and apparatuses configured the baseline heat pump system 104 as two or more subassemblies. Each subassembly included one or more compressors 204 configured to be removed from the front and / or rear ends of the compressor train 202. In some embodiments, each subassembly included one or more flash vessels 212 of the flash vessel train 210. Modifying the baseline heat pump system 104 with the subassemblies altered the compressor train 202, which in turn altered the temperature of the hot water source 110 received by the system 104 and the pressure of the high-pressure steam 140 produced by the system 104. Also, in some embodiments, an alternative subassembly included a smaller, low-flow compressor 204 that was incorporated into the baseline heat pump system 104 to modify the mass flow rate of the high-pressure steam 140 produced by the system 104 while optimizing the COP, cost, and size of the system 104.

[0169] Thus, by modularizing the heat pump system 104, the present disclosure provides a pre-engineered (e.g., pre-configured) and / or factory-manufactured packaged system 104 ready for connection to an existing facility 102.

[0170] Additionally, in some embodiments, the modular construction of the heat pump system 104 allows for the cost and layout footprint of the heat pump system 104 to be optimized for a given application associated with the facility 102, while also providing the standardization necessary to achieve economies of scale during the manufacture of the heat pump system 104. Additionally, in some embodiments, the modular construction of the heat pump system 104 allows for production-level quality and reliability, which is achieved by qualifying two or more subassemblies in addition to qualifying the incoming components of the heat pump system 104.

[0171] Additionally, in some embodiments, the modular configuration of the heat pump system 104 allows for factory fabrication of the heat pump system 104 on one or more skids, transport of the heat pump system 104 from the factory to the facility 102 via standard truck-based transportation, simple and uncomplicated on-site installation of one or more skids at junctions defined by the facility 102, minimizing the footprint, easy removal and / or replacement of subassemblies, or any combination thereof.

[0172] For example, in some embodiments, the footprint of the system 104 (e.g., the surface area below the system 104) is 2,000 square feet (ft 2 )~8,000ft 2 (inclusive), for example, 150 feet long by 50 feet wide. Example 2: Computer system, method and non-transitory computer-readable storage medium for configuring a heat pump system

[0173] In some embodiments, the present disclosure has provided a computer system, a method, and a non-transitory computer-readable storage medium for configuring a heat pump system 104.

[0174] In some embodiments, the computer systems, methods, and non-transitory computer-readable storage media of the present disclosure enable the selection and configuration of one or more subassemblies of the heat pump system 104 to optimally meet a set of predetermined parameter 916 requirements associated with the facility 102.

[0175] In some embodiments, the computer systems, methods, and non-transitory computer-readable storage media of the present disclosure provide a lookup table that is used to match one or more ranges of various required parameters, such as the first temperature of the hot water received from facility 102 and / or the outlet pressure of the high-pressure steam delivered from system 104 to facility 102, to a particular combination of two or more subassemblies configured to operate together.

[0176] In some embodiments, the computer system, method, and non-transitory computer-readable storage medium of the present disclosure evaluated the performance of the heat pump system 104 based on a set of predetermined parameter 916 requirements associated with the facility 102. For example, in some embodiments, the computer system, method, and non-transitory computer-readable storage medium of the present disclosure determined the set of predetermined parameter 916 requirements in a lookup table and then selected two or more subassemblies using the lookup table. In some embodiments, the computer system, method, and non-transitory computer-readable storage medium of the present disclosure evaluated the performance of the heat pump system 104 including two or more subassemblies selected from the lookup table. In some embodiments, the computer system, method, and non-transitory computer-readable storage medium of the present disclosure displayed a report including a complete, pre-qualified configuration of the heat pump system and two or more subassemblies, ready for production, and performance specifications for the configuration. Example 3: Heat pump system

[0177] Referring to FIG. 5A, in some embodiments, the present disclosure has provided a system 104 for generating high-pressure steam.

[0178] In some embodiments, the system 104 included a compressor train 202. The compressor train 202 included a series of at least two compressors 204. In some embodiments, the series of at least two compressors 204 included at least four compressors 204. The compressor train 202 also included a compressor train 202 inlet 216. The compressor train 202 further included a compressor train 202 outlet 208 configured to provide high-pressure steam 140 to the facility 102. In some embodiments, the series of at least two compressors 204 are interposed between the compressor train 202 inlet and the compressor train 202 outlet.

[0179] In some embodiments, the system further included a flash vessel train 210. The flash vessel train 210 included a series of at least two flash vessels 212, and the series of at least two flash vessels further included an end flash vessel 212 located at one end of the flash vessel train 210. In some embodiments, the series of at least two flash vessels 212 included at least four flash vessels 212. A vapor outlet 226 of the end flash vessel 212 was fluidly coupled to an inlet 216 of the compressor train 202. The system 104 further included a vapor outlet 226 of the remainder of the series of at least two flash vessels 212 fluidly coupled between the series of at least two compressors 204.

[0180] In some embodiments, the system 104 is configured to receive hot water at 120°F (48.9°C) from the hot water source 110. In some embodiments, the system 104 is configured to receive steam condensate 214 at 200°F (93.3°C).

[0181] In some embodiments, each of the series of at least two flash vessels 212 in the flash vessel train 210 is configured to maintain its internal pressure below the saturation pressure of the hot water input to each of the flash vessels 212 and to expand the hot water to produce low-pressure steam. For example, in some embodiments, the terminal flash vessel 212-1 is configured to maintain its internal pressure below the hot water saturation pressure of 120°F (48.9°C) (e.g., the saturation pressure of water at 120°F is 116.9 mBar, resulting in an internal pressure of each flash vessel below 116.8 mbar(a)), the second flash vessel 212-2 is configured to maintain its internal pressure below the hot water saturation pressure of 140°F (60°C), the third flash vessel 212-3 is configured to maintain its internal pressure below the hot water saturation pressure of 160°F (71.1°C), and the fourth flash vessel 212-4 is configured to maintain its internal pressure below the hot water saturation pressure of 180°F (82.2°C). Thus, in some embodiments, the internal pressure of the first end flash vessel (e.g., flash vessel 212-1 in any of FIGS. 2A-5B ) is configured to be maintained below the saturation pressure of the hot water from the hot water source 110 received by the system 104. Also, in some embodiments, the internal pressure of the second end flash vessel (e.g., flash vessel 212-2 in any of FIGS. 2A-5B ) is configured to be maintained below the saturation pressure of the steam condensate 214 received by the system 104.

[0182] All references cited herein are incorporated by reference in their entirety for all purposes to the same extent as if each individual publication or patent or patent document were incorporated by reference in its entirety for all purposes.

[0183] The present invention can be implemented as a computer program product that includes a computer program mechanism embedded in a non-transitory computer-readable storage medium. For example, the computer program product can include the program modules shown in any combination of the figures. These program modules can be stored on a CD-ROM, DVD, magnetic disk storage product, USB key, or any other non-transitory computer-readable data or program storage product.

[0184] Many modifications and variations of this invention are possible without departing from the spirit and scope of the invention, as will be apparent to those skilled in the art. The specific embodiments described herein are provided by way of example only. The embodiments were chosen and described in order to best explain the principles of the invention and its practical application, so that others skilled in the art may best utilize the invention and its various embodiments with various modifications as suited to their particular intended uses. The present invention is limited only by the terms of the appended claims, along with the full scope of equivalents to which such claims are entitled.

Claims

1. 1. A system for generating high-pressure steam, comprising: a compressor train and a flash vessel train; the compressor train a series of at least two compressors; an inlet of the compressor train; an outlet of the compressor train configured to supply high pressure steam to a facility; the flash vessel train a series of at least two flash vessels, including an end flash vessel located at one end of the flash vessel train, the vapor outlet of the end flash vessel being fluidly coupled to the inlet of the compressor train; a vapor outlet of the remainder of said series of at least two flash vessels fluidly coupled between said series of at least two compressors.

2. The system of claim 1 , wherein the flash vessel train further comprises an inlet to the flash vessel train configured to receive hot water from the facility or another facility.

3. 3. The system of claim 1, wherein each of the remaining ones of the series of at least two flash vessels includes a liquid outlet fluidly coupled to an inlet of another one of the series of at least two flash vessels.

4. 3. The system of claim 1 or 2, wherein the end flush vessel includes a liquid outlet fluidly coupled to an outlet of the system.

5. 5. The system of claim 4 configured to maintain a temperature range of the flash vessel train in a range between a first temperature of the high pressure steam and a second temperature at the outlet of the system.

6. 3. The system of claim 1, wherein the series of at least two compressors includes centrifugal compressors, and the system further includes a controller configured to prevent stalling or surging in the centrifugal compressors.

7. The system of claim 6 , wherein the controller is configured to maintain pressure at the outlet of the compressor train by varying the rotational speed of each compressor in the compressor train.

8. 3. The system of claim 1 or 2, wherein the end-flush vessel includes a liquid outlet fluidly coupled to a repressurization pump coupled to an outlet of the system.

9. 3. The system of claim 1, wherein each of the series of at least two flash vessels is configured to maintain an internal pressure below the saturation pressure of hot water input to each of the flash vessels and to expand the hot water to produce low-pressure steam.

10. The system of claim 1 or 2, wherein the end flush vessel further comprises an inlet configured to receive hot water from the facility or another facility.

11. The end flush vessel comprises: an inlet configured to receive hot water from the facility or another facility; 3. The system of claim 1 or 2, further comprising: a liquid outlet fluidly coupled to a repressurization pump coupled to an outlet of the system, the outlet of the system being fluidly coupled to a heat exchange mechanism associated with hot water from the facility or another facility.

12. 3. The system of claim 1 or 2, wherein a flash vessel in the flash vessel train includes a continuous blowdown configured to remove contaminants contained in the flash vessel.

13. 3. The system of claim 1 or 2, wherein a flash vessel in the flash vessel train includes a second liquid outlet configured to be fluidly connected to selectively remove fluid from a corresponding flash vessel.

14. 14. The system of claim 13, further comprising a controller in electrical communication with the second liquid outlet, the controller configured to control the selective removal of fluid from the flash vessel.

15. 3. The system of claim 1 or 2, further comprising an attemperator train including at least one attemperator, each attemperator in the attemperator train including an outlet configured to inject warm water received from the facility or another facility into the compressor train.

16. The system of claim 15 , wherein at least one attemperator in the attemperator train is configured to control a flow rate of fluid through the attemperator.

17. 16. The system of claim 15, wherein the controller is configured to modify a flow rate of fluid through the attemperator in accordance with a determination that a temperature and / or pressure associated with the compressor train satisfies a first pressure and / or a first temperature.

18. 3. The system of claim 1, wherein the system has a coefficient of performance greater than 65% of the corresponding Carnot efficiency.

19. 3. The system of claim 1, further comprising a boiler interposed between an output of a terminal compressor in the compressor train and the outlet of the compressor train, and fluidly coupled to the output and the outlet.

20. 3. The system of claim 1, further comprising a vapor accumulator interposed between the output of a terminal compressor in the compressor train and the outlet of the compressor train, and fluidly coupled to the output and the outlet.

21. 3. The system of claim 1 or 2, wherein the compressor train includes between 2 and 20 compressors, both ends included.

22. the compressor train includes m compressors; m is an integer greater than 2 and is selected depending on the temperature of the high-pressure steam and the temperature of hot water received from the facility or another facility; 3. The system according to claim 1 or 2.

23. 3. The system of claim 1 or 2, wherein the series of at least two compressors includes at least four compressors, the at least four compressors arranged to form a herringbone arrangement.

24. 3. The system of claim 1, wherein each compressor in the compressor train has a one-to-one relationship with each flash vessel in the flash vessel train.

25. 3. The system of claim 1, wherein the compressor train includes a first compressor having a first size and a second compressor having a second size smaller than the first size, the first compressor coupled in the compressor train upstream of the second compressor.

26. 26. The system of claim 25, wherein the compressor train includes a third compressor interposed between and fluidly coupled to the first compressor and the second compressor, the third compressor having either the first size or the second size.

27. 3. The system of claim 1 or 2, wherein each compressor in the compressor train has a compression ratio of less than 2.

5.

28. 3. The system of claim 1 or 2, wherein the outlet of the compressor train is configured to supply the high-pressure steam at a pressure between 50 pounds per square inch gauge (PSIg) (3.4 Barg) and 315 PSIg (21.7 Barg), inclusive.

29. 3. The system of claim 1 or 2, further comprising a water loop including a downstream portion configured to receive the hot water from the same or another facility and an upstream portion configured to supply chilled water to the same or another facility, the water loop being heated by the same or another facility.

Images