Systems, methods, and apparatus for generating high pressure steam

Abstract

Systems, methods, and apparatus for generating high pressure steam are provided. A compressor unit includes a series of at least two compressors, an inlet of the compressor unit, and an outlet of the compressor unit. The outlet of the compressor unit is configured to provide high pressure steam to a facility. The flash evaporator group comprises a series of at least two flash evaporators. The series of at least two flash evaporators includes an end flash evaporator at one end of the flash evaporator group. Further, a vapor outlet of the end flash is fluidly coupled to the inlet of the compressor set. In addition, the vapor outlets of the remainder of the series of at least two flashes are fluidly coupled between compressors of the series of at least two compressors.

Description

[0001] CROSS-REFERENCE TO RELATED APPLICATIONS

[0002] This application claims priority to U.S. Provisional Patent Application No. 63 / 371,837, filed on August 18, 2022, entitled “Steam Generating Mechanical Vapor Recompression Heat Pump,” which is hereby incorporated by reference in its entirety for all purposes. Technical Field

[0003] The present disclosure generally relates to systems, methods, and apparatus for generating high pressure steam. Background Art

[0004] Reducing on-site emissions in the industrial sector is critical to achieving desired greenhouse gas targets. For example, a set of greenhouse gas targets is set forth in the California Air Resources Board's AB32 and SB 32 greenhouse gas reduction targets, but this particular set of greenhouse gas targets should not be considered the only targets to be met in the industrial sector. Currently, industrial manufacturing plants burn natural gas in steam boilers to evaporate water and produce steam. Once the thermal energy of the steam is used advantageously, the thermal energy is removed from the process via a cooling water loop. This increases the temperature of the cooling water. The heated cooling water is then typically sent to a cooling tower, where the thermal energy is discharged to the atmosphere, i.e., thrown away, in order to reduce the temperature of the cooling water.

[0005] In order to reach greenhouse gas targets and become carbon neutral, there is a need to increase industrial electrification. This includes electrification of natural gas driven boilers in various industries. For example, industrial sectors that have been specifically identified for improvement include natural gas boilers used to generate steam in the chemical sector, in the pulp and paper sector, associated with food production, and in other various industrial sectors. It is believed that these sectors and others may be closer to meeting energy targets.

[0006] The obstacle to achieving the desired energy target is the lack of effective and economically attractive technology to electrify the large amount of thermal energy demand associated with steam generation in the industry including the above-mentioned sectors. Today's most advanced industrial heat pumps are unable to reach the temperature required for the production of medium and high pressure saturated steam required for many industrial facilities. On the other hand, the most advanced electric boiler technology can indeed reach the required temperature and pressure, but they reach the required temperature and pressure with a low performance coefficient (COP) of 1.0 or less. This leads to excessive power consumption, making these systems uneconomical to operate. In addition, high power consumption may add excessive pressure to the power grid.

[0007] It would also be desirable that the development of alternative electric boiler technologies that meet medium and high pressure saturated steam requirements could be implemented with limited custom engineering and specialized one-off field assembly. Custom engineering and specialized field assembly greatly limit availability and increase costs. This in turn is believed to affect industrial customers' perception of reliability. Furthermore, custom solutions with specialized field assembly may often experience very expensive downtime, and therefore industrial customers are reluctant to try new technologies that may be perceived as likely to fail and / or result in undesirable downtime.

[0008] The most advanced heat pumps currently available typically use hydrofluorocarbon (HFC) or hydrofluoroolefin (HFO) refrigerants to generate thermal energy at temperatures up to 320°F. These known systems are not capable of directly generating steam, but must be used in combination with an unfired steam generator, which introduces a nominal temperature drop of 20°F. Therefore, the maximum saturated steam pressure that these systems can generate is 3.5 barg (50 psig), which is not high enough to address the medium pressure (3.5 barg to 20 barg) applications required throughout the manufacturing industry. In addition, these systems have a relatively low coefficient of performance of <3.0, resulting in high power requirements and high operating costs. HFC refrigerants have high global warming potential values, and HFO refrigerants have low global warming potential values ​​but high costs.

[0009] CO2-based heat pumps also utilize a low-cost and low-global warming potential refrigerant (CO2), but are limited to temperatures of approximately 238°F or less due to the very high pressures required for the refrigerant. Although 238°F is above the atmospheric boiling point of water, CO2-based heat pumps are not able to generate steam because they require a low fluid return temperature of 203°F or less, and the fluid return temperature typically determines the ability to drive a steam generator.

[0010] Ammonia-based heat pumps are a more mature technology, but like CO2-based heat pumps, the high pressure nature of the system is limited to a maximum output temperature of approximately 203°F, which is not suitable for steam generation. Ammonia-based systems can produce lower temperatures, and therefore, ammonia-based systems are complementary to, rather than competitive with, heat pump systems required for steam generation. For example, ammonia-based systems are commonly used to provide low temperature refrigeration in the food production industry, and typically reject waste heat at temperatures in the range of approximately 85°F to 100°F.

[0011] There is a need for an improved arrangement that addresses at least one or more of the above-mentioned disadvantages in a manner that is cost-effective, efficient, reliable, scalable, etc., as well as providing other features and benefits. Summary of the invention

[0012] In view of the above background, there is a need in the art for systems, methods, and apparatuses that electrify high pressure steam generation. Various embodiments of the present application are efficient in terms of energy consumption and manufacturing costs.

[0013] Therefore, various aspects of the present disclosure relate to systems, methods and equipment for producing high-pressure steam. For example, in some embodiments, the systems, methods and equipment of the present disclosure are configured as heat pumps. In some embodiments, the heat pumps of the systems, methods and equipment of the present disclosure are configured as open cycle mechanical vapor recompression, high-pressure steam generation heat pumps. In some embodiments, the systems, methods and equipment of the present disclosure are configured to replace conventional fossil fuel (e.g., natural gas) boilers and / or conventional evaporative cooling towers, which not only reduce total energy consumption but also provide water conservation. More particularly, in some embodiments, the systems, methods and equipment of the present disclosure provide high-efficiency high-pressure heat pumps, which provide high-pressure steam by receiving hot water (e.g., cooling water from facilities) into flasher groups, and the flasher groups are maintained at a pressure lower than the saturation pressure of the hot water, so as to cool the hot water and produce steam (e.g., low-pressure steam) at the same time. The flasher group is configured to supply low-pressure steam to the compressor group, and the compressor group is configured to compress the low-pressure steam produced by the flasher group to produce high-pressure steam at the desired pressure of the facility. Thus, in some embodiments, the systems, methods, and apparatus of the present disclosure generate high pressure steam having a temperature of up to 426 degrees Fahrenheit (℉) (219 degrees Celsius (℃)), a pressure of up to 315 pounds per square inch gauge (PSI) (19.0 Barg), and a temperature rise of up to 330℉ (166℃).

[0014] In addition, in some embodiments, the systems, methods, and apparatus of the present disclosure provide a baseline heat pump system that can be modularly configured based on interchangeable subassemblies of the compressor group and / or flasher group of the heat pump system. Therefore, in some embodiments, the systems, methods, and apparatus of the present disclosure provide a stand-alone heat pump that is not deeply integrated into the process associated with the facility. Instead, the systems, methods, and apparatus of the present disclosure connect to the facility at a standard portion containing a hot water source and a steam main, while operating otherwise outside the process associated with the facility.

[0015] Turning to a more specific aspect, one aspect of the present disclosure relates to providing a system for producing high pressure steam. The system comprises a compressor group. The compressor group comprises a series of at least two compressors. In addition, the compressor group comprises an inlet of the compressor group. In addition, the compressor group comprises an outlet of the compressor group, and the outlet is configured to provide high pressure steam to the facility. The system further comprises a flasher group. The flasher group comprises a series of at least two flashers, wherein the series of at least two flashers further comprises a terminal flasher at one end of the flasher group. In addition, the vapor outlet of the terminal flasher is fluidly coupled to the inlet of the compressor group. In addition, the system comprises a vapor outlet of the remainder of the series of at least two flashers, and the vapor outlet is fluidly coupled between the compressors in the series of at least two compressors.

[0016] In some embodiments, the flasher bank further comprises an inlet of the flasher bank configured to receive hot water received from the facility or a different facility.

[0017] In some embodiments, the remainder of the series of at least two flashers each comprises a liquid outlet fluidly coupled to an inlet of another one of the series of at least two flashers.

[0018] In some embodiments, the tip flasher includes a liquid outlet fluidly coupled to an outlet of the system.

[0019] In some embodiments, the system further comprises a controller configured to maintain a temperature range of the flasher group between a temperature of the high pressure steam and a temperature of an outlet of the system.

[0020] In some embodiments, the series of at least two compressors comprises a centrifugal compressor.In some embodiments, the controller is configured to maintain the centrifugal compressor from blocking or surging.

[0021] In some embodiments, the terminal flasher comprises a liquid outlet fluidly coupled to a reboost pump. The reboost pump is coupled to an outlet of the system.

[0022] In some embodiments, each flasher in a series of at least two flashers is configured to maintain an internal pressure less than the saturation pressure of the hot water input into the corresponding flasher. In addition, each flasher in a series of at least two flashers is configured to expand the hot water to produce low-pressure steam.

[0023] In some embodiments, the terminal flasher further comprises an inlet configured to receive hot water. The hot water is received from the facility or a different facility.

[0024] In some embodiments, the terminal flasher further comprises an inlet configured to receive hot water received from the facility or a different facility. In addition, the terminal flasher further comprises a liquid outlet fluidly coupled to a reboost pump. The reboost pump is further coupled to an outlet of the system. In addition, the outlet of the system is fluidly coupled to a heat exchange mechanism associated with the hot water received from the facility or a different facility.

[0025] In some embodiments, the system further comprises a desuperheater group, the desuperheater group comprising at least one desuperheater. Each desuperheater in the desuperheater group comprises an outlet configured to inject hot water received from the facility or a different facility into the compressor group.

[0026] In some embodiments, at least one desuperheater in the desuperheater bank is configured to control a flow rate of a fluid through the desuperheater.

[0027] In some embodiments, based on a determination that a temperature and / or pressure associated with the compressor train satisfies a first pressure and / or a first temperature, the controller is configured to modify a flow rate of the fluid through the desuperheater.

[0028] In some embodiments, the system comprises a coefficient of performance greater than 65% of the corresponding Carnot efficiency.

[0029] In some embodiments, a flasher in the flasher bank comprises a continuous blowdown. The continuous blowdown is configured to remove contaminants contained by the flasher.

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

[0031] In some embodiments, the system further includes a steam accumulator disposed to be interposed between and fluidly coupled to the output of the terminal compressor in the compressor train and the outlet of the compressor train.

[0032] In some embodiments, the compressor train includes between two and twenty compressors, inclusive.

[0033] In some embodiments, the compressor group comprises m compressors, wherein m is an integer greater than 2. Furthermore, m is selected based on the temperature of the high pressure steam and the temperature of the hot water received from the facility or a different facility.

[0034] In some embodiments, each compressor in the compressor train and each flasher in the flasher train share a one-to-one relationship.

[0035] In some embodiments, the compressor train includes a first compressor and a second compressor. The first compressor includes a first size, and the second compressor includes a second size that is smaller than the first size. In addition, the first compressor is coupled upstream of the second compressor in the compressor train.

[0036] In some embodiments, the compressor train includes a third compressor interposed between and fluidly coupled to the first and second compressors. The third compressor includes a first size or a second size.

[0037] In some embodiments, each compressor in the compressor train comprises a compression ratio of less than 2.5.

[0038] In some embodiments, the outlet of the compressor train 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.

[0039] In some embodiments, the controller is configured to modify the rotational speed of respective compressors in the compressor train, thereby maintaining a pressure at an outlet of the compressor train.

[0040] In some embodiments, a flasher in the flasher bank includes a second liquid outlet fluidly configured to selectively remove fluid from a corresponding flasher.

[0041] In some embodiments, the system further comprises a controller in electronic communication with the second liquid outlet. In some such embodiments, the controller is configured to control the selective removal of fluid from the flasher.

[0042] In some embodiments, based on a determination that a temperature and / or pressure associated with the compressor train satisfies a first pressure and / or a first temperature, the controller is configured to modify a flow rate of the fluid through the desuperheater.

[0043] In some embodiments, the series of at least two compressors comprises at least four compressors. In some such embodiments, the at least four compressors are arranged in a herringbone array configuration.

[0044] In some embodiments, the system further comprises a water circuit. In some embodiments, the water circuit comprises an upstream portion and a downstream portion. In some embodiments, the downstream portion is configured to receive hot water from the same facility or a different facility. In some embodiments, the upstream portion is configured to supply cooling water to the same facility or a different facility. In addition, in some embodiments, the water circuit is heated by the same facility or a different facility.

[0045] The systems, methods, and apparatus of the present disclosure have other features and advantages that will be apparent from or set forth in more detail in the accompanying drawings and the following detailed description incorporated herein, which together serve to explain certain principles of the invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0046] Figure 1A is a block diagram of an example high pressure steam generating heat pump system according to some embodiments, wherein dashed boxes represent optional elements.

[0047] Figure 1B is a block diagram of an example high pressure steam generating heat pump system according to some embodiments, wherein dashed boxes represent optional elements.

[0048] Figure 2A , Figure 2B , Figure 3 , Figure 4 , Figure 5A , Figure 5B and Figure 5C is a block diagram of an example high pressure steam generating heat pump system according to some embodiments, wherein dashed boxes represent optional elements.

[0049] Figure 6 Graphs depicting various parameters associated with various high pressure steam generating heat pump systems according to some embodiments.

[0050] Figure 7 Graphs depicting the performance of a high pressure steam generating heat pump system according to some embodiments compared to various conventional techniques.

[0051] Figure 8 is a flow chart of an example method for generating high pressure steam according to some embodiments, wherein dashed boxes represent optional elements in the flow chart.

[0052] Fig. 9 FIG. 1 is a block diagram illustrating an example computer system used in a high pressure steam generation heat pump system according to some embodiments.

[0053] In the drawings, reference numbers refer to the same or equivalent parts of the present invention throughout the several figures of the drawing. DETAILED DESCRIPTION

[0054] Provide a system, method and apparatus for producing high pressure steam. A compressor unit comprises a series of at least two compressors, an inlet of the compressor unit and an outlet of the compressor unit. In some embodiments, each compressor in the compressor unit is a centrifugal compressor. The outlet of the compressor unit is configured to provide high pressure steam to the facility, which allows the compressor unit to be coupled to the facility. In some embodiments, the compressor unit is coupled (e.g., directly connected) to the facility. A flasher unit comprises a series of at least two flashers. A series of at least two flashers are included in a terminal flasher at one end of the flasher unit. In some embodiments, the flasher unit is configured to convert the heat associated with the hot water received by the system into latent heat. In addition, the vapor outlet of the terminal flasher is fluidly coupled to the inlet of the compressor unit. In addition, the system comprises a series of vapor outlets of the rest of at least two flashers, and the vapor outlet is fluidly coupled between the compressors in the series of at least two compressors. In this way, each flasher in the flasher unit produces low pressure steam, which is received by the corresponding compressor in the compressor unit so as to increase the pressure of the low pressure steam, for example, so as to produce high pressure steam.

[0055] Reference will now be made in detail to the embodiments, examples of which are shown in the accompanying drawings. In the following detailed description, numerous specific details are set forth in order to provide a thorough understanding of the present disclosure. However, it will be apparent to one of ordinary skill in the art that the present disclosure may be practiced without these specific details. In other cases, well-known methods, procedures, and components have not been described in detail in order to avoid unnecessarily obscuring aspects of the embodiments.

[0056] It should be understood that although the terms first, second, etc. may be used herein to describe various elements, these elements should not be limited by these terms. These terms are only used to distinguish one element from another element. For example, without departing from the scope of the present disclosure, the first compressor may be referred to as the second compressor, and similarly, the second compressor may be referred to as the first compressor. Both the first compressor and the second compressor are compressors, but they are not the same compressor.

[0057] The terms used in this disclosure are only for the purpose of describing specific embodiments, and are not intended to limit the present invention. As used in the description of the present invention and the appended claims, unless the context clearly indicates otherwise, the singular forms "a", "an" and "said" are intended to also include plural forms. It will also be understood that the term "and / or" as used herein refers to and covers any and all possible combinations of one or more of the associated listed items. It will be further understood that the terms "comprises" and / or "comprising" when used in this specification specify the presence of stated features, integers, steps, operations, elements and / or components, but do not exclude the presence or addition of one or more other features, integers, steps, operations, elements, components and / or groups thereof.

[0058] The foregoing description includes example systems, methods, techniques, instruction sequences, and computing machine program products that embody illustrative embodiments. For purposes of explanation, a number of specific details are set forth in order to provide an understanding of the various embodiments of the subject matter of the present invention. However, it will be apparent to those skilled in the art that the embodiments of the subject matter of the present invention may be practiced without these specific details. In general, well-known instruction examples, protocols, structures, and techniques have not been shown in detail.

[0059] For purposes of explanation, the foregoing description has been described with reference to specific embodiments. However, the following illustrative discussion is not intended to be exhaustive or to limit the embodiments to the precise form disclosed. In view of the above teachings, many modifications and variations are possible. The embodiments are selected and described in order to best explain the principles and their practical application, thereby enabling others skilled in the art to best utilize the embodiments and various embodiments with various modifications suitable for the intended specific use.

[0060] For the sake of clarity, not all conventional features of the embodiments described herein are shown and described. It will be appreciated that in the development of any such actual embodiment, a large number of implementation-specific decisions are made in order to achieve the designer's specific goals, such as compliance with use case and business-related constraints, and these specific goals will vary from one embodiment to another and from one designer to another. Furthermore, it will be appreciated that such design work may be complex and time consuming, but is still a routine engineering task for those skilled in the art having the benefit of this disclosure.

[0061] 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 [a stated condition or event] is detected" may be interpreted to mean "upon determining" or "in response to determining" or "upon detecting [a stated condition or event]" or "in response to detecting [a stated condition or event]," depending on the context.

[0062] As used herein, the term "about" or "approximately" may mean within an acceptable error range of a particular value determined by one of ordinary skill in the art, which may depend in part on how the value is measured or determined, such as limitations of the measurement system. For example, according to practice in the art, "about" may mean within 1 or more than 1 standard deviation. "About" may mean a range of ±20%, ±10%, ±5%, or ±1% of a given value. In the case of describing specific values ​​in the present application and claims, unless otherwise stated, the term "about" means within an acceptable error range of a particular value. The term "about" may have a 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%.

[0063] As used herein, the term "period" means a predefined period of time.

[0064] Furthermore, unless expressly stated otherwise, the terms "compressor" and "blower" are used interchangeably herein.

[0065] Unless expressly stated otherwise, the terms "flash vessel" and "knockout drum" are used interchangeably herein.

[0066] Unless expressly stated otherwise, the terms "steam" and "water vapor" are used interchangeably herein.

[0067] Furthermore, the term "stream" as used herein means any material that is moving, directly or indirectly, from one location to another or that is on its way, directly or indirectly, from one location to another. In some embodiments, a stream is still a stream even if it is temporarily stationary for any period of time. In some embodiments, it will be understood that if the present disclosure refers to a particular stream, this does not necessarily refer to a single pipeline or other physical transport.

[0068] In addition, when a reference numeral is given an "i-th" designation, the reference numeral refers to a common component, set, or embodiment. For example, a compressor referred to as "compressor i" refers to the i-th compressor in a plurality of compressors (e.g., compressor 204-i in a plurality of compressors 204).

[0069] Figure 1Aand Figure 1B Each represents a block diagram of an example high pressure steam generating heat pump system according to some embodiments, where dashed boxes represent optional elements. Figures 2A to 5C FIG. 1 is a block diagram of a detailed example high pressure steam generating heat pump system according to some embodiments, wherein dashed boxes represent optional elements. Figure 1A and Figure 1B In some embodiments, the present disclosure relates to providing a method for producing high pressure steam (e.g., Figure 1A High pressure steam 140-1 or 140-2, Figure 1B High pressure steam 140, Figures 2A to 7 any one of the high pressure steam 140, etc.) system (e.g., Figures 1A to 7 system 104 of any one of the above).

[0070] In some embodiments, system 104 is coupled to one or more facilities (e.g., Figure 1A The first facility 102-1, Figure 1B For example, in some embodiments, the system 104 is associated with and positioned near the first facility 102-1, which allows the system 104 to utilize one or more resources from the first facility 102-1. In addition, in some embodiments, the system 104 is associated with and positioned near the first facility 102-1 to allow the system 104 to provide the high-pressure steam 140 generated at the system 104 to the first facility 102-1, such as by coupling to an existing steam main of the first facility 102-1. However, the present disclosure is not limited thereto.

[0071] refer to Figures 2A to 5C , the system 104 includes a compressor unit (e.g., Figures 2A to 5C Any of the compressor group 202, etc.) and the flash evaporator group (e.g., Figure 1A to Figure 5B , the system 104 collectively utilizes the compressor group and the flasher group to generate high-pressure steam 140 for the facility 102.

[0072] Those skilled in the art of the present disclosure will appreciate that temperature rise and mechanical stresses within the respective compressors limit the maximum pressure differential provided by any stage of the respective compressors. Therefore, in order to provide high pressure steam 140 that can be utilized by the facility 102, the compressor train 202 includes a series of at least two compressors (e.g., Figures 2A to 5C A first compressor 204-1 of any one of Figures 2A to 5C The second compressor 204-2 of any one of Figures 3 to 5C The third compressor 204-3 of any one of the Figure 5CFor example, in some embodiments, the compressor group 202 includes between two and twenty compressors 204 (e.g., two compressors 204, three compressors 204, . . . twenty compressors 204, etc.), between two and seventeen compressors 204, between two and fifteen compressors 204, between two and twelve compressors 204, between two and nine compressors 204, between two and six compressors 204, between two and three compressors 204, between three and twenty compressors 204, between three and seventeen compressors 204, between three and fifteen compressors 204, between three and twelve compressors 204, between three and nine compressors 204, between three and six compressors 204, between five and twenty compressors 204, between five and seventeen compressors 204, between five and fifteen compressors 204, between five and twelve compressors 204, between five and nine compressors 204, between two and six compressors 204, between two and three compressors 204, between three and twenty compressors 204, between three and seventeen compressors 204, between five and fifteen compressors 204, between five and twelve compressors 204, between five and nine compressors 204, between 04, between five and six compressors 204, between seven and twenty compressors 204, between seven and seventeen compressors 204, between seven and fifteen compressors 204, between seven and twelve compressors 204, between seven and nine compressors 204, between nine and twenty compressors 204, between nine and seventeen compressors 204, between nine and fifteen compressors 204, between nine and twelve compressors 204, between eleven and twenty compressors 204, between eleven and seventeen compressors 204, between eleven and fifteen compressors 204, between eleven and twelve compressors 204, between thirteen and twenty compressors 204, between thirteen and seventeen compressors 204, between thirteen and fifteen compressors 204, between fifteen and twenty compressors 204, between fifteen and seventeen compressors 204, or between seventeen and twenty compressors 204, inclusive. In some embodiments, the compressor group 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 twelve 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, the compressor group 202 includes at most two compressors 204, at most three compressors 204, at most four compressors 204, at most five compressors 204, at most six compressors 204, at most seven compressors 204, at most eight compressors 204, at most nine compressors 204, at most ten compressors 204, at most eleven compressors 204, at most twelve compressors 204, at most thirteen compressors 204, at most fourteen compressors 204, at most fifteen compressors 204, at most sixteen compressors 204, at most seventeen compressors 204, at most eighteen compressors 204, at most nineteen compressors 204 or at most twenty compressors 204.

[0073] In some embodiments, compressor group 202 includes m compressors 204, where m is an integer, such as an integer greater than two. In some embodiments, m is at least two and less than twenty-one. In addition, in some embodiments, based on one or more input parameters of system 104 (e.g., Fig. 9m is selected for the system 104 based on a parameter 916 of the system 104 and / or one or more output parameters 916 of the system 104. For example, in some embodiments, m is selected based on a temperature of the high pressure steam 140 generated by the system 104 and a temperature of hot water received by the system 104 from the facility 102 or a different facility 102. In some embodiments, m is selected based on a rise (e.g., a difference) between a temperature of the high pressure steam 140 generated by the system 104 and a temperature of hot water received by the system 104 from a hot water source 110 associated with the facility 102 or a different facility 102. For example, in some embodiments, m is selected to provide between 60°F (15.6°C) and 330°F (165°C), between 60°F (15.6°C) and 300°F (149°C), between 60°F (15.6°C) and 270°F (135°C), between 60°F (15.6°C) and 250°F (121°C), between 60°F (15.6°C) and 220°F (65.6°C), between 60°F (15.6°C) and 205°F (96.1°C), between 60°F (15.6°C) and 190°F (87.8°C), between 60°F (15.6°C) and 250°F (121°C), between 60°F (15.6°C) and 220°F (65.6°C), between 60°F (15.6°C) and 205°F (96.1°C), between 60°F (15.6°C) and 190°F (87.8°C), between 60°F (15.6°C) and 250°F (121°C). ) and 175℉(79.4℃), 60℉(15.6℃) and 150℉(65.6℃), 60℉(15.6℃) and 135℉(57.2℃), 60℉(15.6℃) and 120℉(48.9℃), 60℉(15.6℃) and 105℉(40.6℃), 60℉(15.6℃) and 90℉(32.2℃), 60℉(15.6℃) and 75℉(23.9℃), 80℉(26.7℃) and 330℉(165℃), 80℉(26.7℃) and 30 0℉(149℃), 80℉(26.7℃) and 270℉(135℃), 80℉(26.7℃) and 250℉(121℃), 80℉(26.7℃) and 220℉(65.6℃), 80℉(26.7℃) and 205℉(96.1℃), 80℉(26.7℃) and 190℉(87.8℃), 80℉(26.7℃) and 175℉(79.4℃), 80℉(26.7℃) and 150℉(65.6℃), 80℉(26.7℃) and 135℉(5 7.2℃), between 80℉(26.7℃) and 120℉(48.9℃), between 80℉(26.7℃) and 105℉(40.6℃), between 80℉(26.7℃) and 90℉(32.2℃), between 100℉(37.8℃) and 330℉(165℃), between 100℉(37.8℃) and 300℉(149℃), between 100℉(37.8℃) and 270℉(135℃), between 100℉(37.8℃) and 250℉(121℃), between 100℉(37.8℃) and 220℉(65.6℃), between 100℉(37.8℃) and 205℉(96.1℃), between 100℉(37.8℃) and 190℉(87.8℃), between 100℉(37.8℃) and 175℉(79.4℃), between 100℉(37.8℃) and 150℉(65.6℃), between 100℉(37.8℃) and 135℉(57.2℃), between 100℉(37.8℃) and 120℉(48.9℃), between 100℉(37.8℃) and 105℉(40.6℃), between 120℉(48.9℃) and 330℉(165℃), between 120℉(48.9℃) and 300℉(149℃), between 120℉(48.9℃) 120℉(48.9℃) and 270℉(135℃), 120℉(48.9℃) and 250℉(121℃), 120℉(48.9℃) and 220℉(65.6℃), 120℉(48.9℃) and 205℉(96.1℃), 120℉(48.9℃) and 190℉(87.8℃), 120℉(48.9℃) and 175℉(79.4℃), 120℉(48.9℃) and 150℉(65.6℃), 120℉(48.9℃) and 135℉(57.2℃), 140℉(60.0℃) and 330℉(165℃), 140℉(60.0℃) and 300℉(149℃), 140℉(60.0℃) and 190℉(87.8℃), 120℉(48.9℃) and 175℉(79.4℃), 120℉(48.9℃) and 150℉(65.6℃), 120℉(48.9℃) and 135℉(57.2℃), 140℉(60.0℃) and 270℉(135℃), 140℉(60.0℃) and 250℉(121℃), 140℉(60.0℃) and 220℉(65.6℃), 140℉(60.0℃) and 205℉(96.1℃), 140℉(60.0℃) and 190℉(87.8℃), 140℉(60.0℃) and 175℉(79.4℃), 140℉(60.0℃) and 150℉(65.6℃), 175℉(79.4℃) and 330℉(165℃), 175℉(79.4℃) and 300℉(149℃), 175℉(79.4℃) and 270℉(135℃) , between 175℉(79.4℃) and 250℉(121℃), between 175℉(79.4℃) and 220℉(65.6℃), between 175℉(79.4℃) and 205℉(96.1℃), between 175℉(79.4℃) and 190℉(87.8℃), between 190℉(87.8℃) and 220℉(65.6℃), between 190℉(87.8℃) and 330℉(165℃), between 190℉(87.8℃) and 300℉(149℃), between 190℉(87.8℃) and 270℉(135℃), between 190℉(87.8℃) and 250℉(121℃), between 190℉(87.8℃) and 205℉(96.1℃), between 175℉(79.4℃) and 190℉(87.8℃), between 190℉(87.8℃) and 220℉(65.6℃), between 190℉(87.8℃) and 330℉(165℃), between 190℉(87.8℃) and 300℉(149℃), between 190℉(87.8℃) and 270℉(135℃), between 190℉(87.8℃) and 250℉(121℃), between 190℉(87.8℃) and 2(165°C), between 205°F (96.1°C) and 330°F (165°C), between 205°F (96.1°C) and 300°F (149°C), between 205°F (96.1°C) and 270°F (135°C), between 205°F (96.1°C) and 250°F (121°C), between 205°F (96.1°C) and 220°F (65.6°C), between 250°F (121°C) and 330°F (165°C), between 250°F (121°C) and 300°F (149°C), between 250°F (121°C) and 270°F (135°C), or between 270°F (135°C) and 330°F (165°C), inclusive. In some embodiments, m is selected to provide a temperature of at least 60°F (15.6°C), at least 65°F (18.3°C), at least 70°F (21.1°C), at least 75°F (23.9°C), at least 80°F (26.7°C), at least 85°F (29.4°C), at least 90°F (32.2°C), at least 95°F (35.0°C), at least 100°F (37.8°C), at least 105°F (40.6°C), at least 110°F (43.3°C), at least 115°F (46.1°C), at least 120°F (48.9°C), at least 125°F (51.7°C), at least 130°F (54.4°C), at least 135°F (57.2°C), at least 140°F (60.0°C), at least 145°F (62.8°C), at least 150°F (63.9°C), at least 151°F (64.7°C), at least 152°F (65.9°C), at least 153°F (66.8°C), at least 154°F (67.9°C), at least 156°F (68.9°C), at least 157°F (69.9°C), at least 161°F (70.0°C), at least 162°F (71.9°C), at least 164°F (73.9°C), at least 165°F (75. at least 150°F (65.6°C), at least 155°F (68.3°C), at least 160°F (71.1°C), at least 165°F (73.9°C), at least 170°F (76.7°C), at least 175°F (79.4°C), at least 180°F (82.2°C), at least 185°F (85.0°C), at least 190°F (87.8°C), at least 195°F (90.6°C), at least 200°F (93.3°C), at least 205°F (96.1°C), at least 210°F (98.9°C), at least 215°F (102°C), at least 220°F (104°C), at least 250°F (121°C), at least 270°F (135°C), at least 300°F (149°C), or at least 330°F (165°C). In some embodiments, m is selected to provide a maximum temperature of 60°F (15.6°C), a maximum temperature of 65°F (18.3°C), a maximum temperature of 70°F (21.1°C), a maximum temperature of 75°F (23.9°C), a maximum temperature of 80°F (26.7°C), a maximum temperature of 85°F (29.4°C), a maximum temperature of 90°F (32.2°C), a maximum temperature of 95°F (35.0°C), a maximum temperature of 100°F (37.8°C), a maximum temperature of 105°F (40.6°C), a maximum temperature of 110°F (43.3°C), a maximum temperature of 115°F (46.1°C), a maximum temperature of 120°F (48.9°C), a maximum temperature of 125°F (51.7°C), a maximum temperature of 130°F (54.4°C), a maximum temperature of 135°F (57.2°C), up to 140°F (60.0°C), up to 145°F (62.8°C), up to 150°F (65.6°C), up to 155°F (68.3°C), up to 160°F (71.1°C), up to 165°F (73.9°C), up to 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 1 90°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).

[0074] In some embodiments, the series of at least two compressors 204 is configured such that at least two compressors 204 in the series of at least two compressors 204 are fluidly coupled in series. In some embodiments, the series of at least two compressors 204 are at least partially fluidly coupled in series, which allows a medium flow to flow from a first compressor 204-1 in the series of at least two compressors 204 to a second compressor 204-2 in the series of at least two compressors 204. For example, in some embodiments, when the series of at least two compressors 204 are at least partially fluidly coupled in series, the series of at least two compressors 204 includes a trace through both the first compressor 204-1 and the second compressor 204-2. In some embodiments, the series of at least two compressors 204 is configured such that each compressor in the series of at least two compressors 204 is arranged in a straight line, a substantially straight line, an arc, or a substantially arc. In some embodiments, the series of at least two compressors 204 is configured such that each compressor in the series of at least two compressors 204 is arranged in an array, such as an array of two or more rows of parallel or substantially parallel lines. For example, in some embodiments, the series of at least two compressors 204 are configured such that each compressor in the series of at least two compressors 204 is arranged in a herringbone array, wherein a first line associated with a first set of compressors 204 in the series of at least two compressors 204 has a first slope, and a second set of compressors 204 in the series of at least two compressors 204 has a second slope opposite to the first slope. As a non-limiting example, briefly refer to Figure 5C In some embodiments, the series of at least two compressors 204 includes at least four compressors 204 (e.g., Figure 5BIn some such embodiments, at least four compressors 204 in the compressor group 202 are arranged in a herringbone array configuration, so that the outlet of the first compressor set 204 in a series of at least four compressors 204 has a first slope, and the second compressor set 204 in a series of at least four compressors 204, wherein the second slope is tangential, substantially tangential, orthogonal or substantially orthogonal to the first slope. In some embodiments, the second slope is the reciprocal of the first slope. In some embodiments, the first slope has a 45-degree difference with the second slope or has a substantially 45-degree difference with the second slope. In some embodiments, the herringbone configuration of the compressor group 202 is configured so that the steam generated by each compressor 204 flows in a first direction. In some such embodiments, the first compressor set 204 in a series of at least four compressors 204 is configured to change the direction of flow in a second direction, and the second compressor set 204 in a series of at least four compressors 204 is configured to change the direction of flow in a third direction, wherein the first direction, the second direction and the third direction are each different directions. For example, in some embodiments, the herringbone configuration of the compressor group 202 is configured such that the steam generated by each compressor 204 flows in a first horizontal direction, the first compressor group 204 in the series of at least four compressors 204 is configured to change the direction of the flow in a second vertical direction, and the second compressor group 204 in the series of at least four compressors 204 is configured to change the direction of the flow in a third vertical direction, wherein the second vertical direction and the third vertical direction are different. In some embodiments, the second vertical direction is consistent with gravity (e.g., Figure 5C g, which has access to Figure 5CThe vector direction of the page is opposite, and the third vertical direction has gravity. However, the present disclosure is not limited to this. In some embodiments, the herringbone configuration of the compressor group 202 is configured so that the steam 140, 206 generated by each compressor 204 flows in a first horizontal direction, the first compressor set 204 in a series of at least four compressors 204 is configured to change the direction of the flow in a second horizontal direction, and the second compressor set 204 in a series of at least four compressors 204 is configured to change the direction of the flow in a third horizontal direction, wherein the second horizontal direction and the third horizontal direction are different. In some embodiments, the herringbone configuration is configured to maintain the flow through the compressor group 204 at a constant or substantially constant height so that a uniform or substantially uniform gravity is applied to the compressor group 202. In some embodiments, the herringbone configuration of the compressor group 202 is configured to provide an array of compressors arranged around a line (Y), wherein each compressor 204 in the compressor group 202 is arranged at a unique position around the line according to a first constant amplitude and a first constant frequency. For example, in some embodiments, the herringbone configuration of compressor bank 202 is configured to provide an array of compressors arranged according to the following function:

[0075] Y=B+(A*sin(k*X)), where Y is the first position of the corresponding compressor 204 in the compressor group 202, B is the position of the terminal compressor 204 of the compressor group 202, A is a constant amplitude, k is a constant frequency, and X is the second position of the corresponding compressor. However, the present disclosure is not limited thereto.

[0076] In some embodiments, the compressor group 202 includes a first compressor 202-1 and a second compressor 202-2. The first compressor 202-1 includes a first optimal inlet volume flow rate. In addition, in some such embodiments, the second compressor 202-2 includes a second optimal inlet volume flow rate that is greater than the first optimal inlet volume flow rate of the first compressor 202-1. In addition, in some such embodiments, the first compressor 204-1 is coupled upstream of the second compressor 204-2 in the compressor group 202.

[0077] refer to Figure 2A and Figure 2BIn 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 different from the first diameter. In some embodiments, the first diameter is greater than the second diameter. In some embodiments, the first diameter is the same as the second diameter. For example, in some embodiments, the first diameter is a number k selected between 0.1 meters and 1.6 meters, and the second diameter is a number l selected between 0.1 meters and 1.6 meters, where k and l are different numbers. However, the present disclosure is not limited thereto. In some embodiments, the third compressor 204-3 has a second diameter and / or a third diameter greater than the second diameter. In some such embodiments, the third compressor is placed 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 inserted between the first compressor 204-1 and the second compressor 204-2 and is fluidically coupled to the first compressor 204-1 and the second compressor 204-2. In some embodiments, the third compressor is fluidically coupled to the first compressor 204-1 and the second compressor 204-2 in series. However, the present disclosure is not limited thereto.

[0078] In some embodiments, the compressor group 202 includes a third compressor 204-3, which is adjacent to the first compressor 204-1 and the second compressor 204-2 and inserted between the first compressor 204-1 and the second compressor 204-2. Figure 4 The compressor unit 202 includes a second compressor 204-2, which is adjacent to Figure 4 The first compressor 204-1 and the third compressor 204-3 of the system 104 are inserted between the first compressor 204-1 and the third compressor 204-3. However, the present disclosure is not limited thereto. In some embodiments, the third compressor 204-3 includes a first optimal inlet volume flow rate or a second optimal inlet volume flow rate.

[0079] In some embodiments, each compressor 204 in the compressor group 202 includes a compression ratio of less than 2.5. For example, in some embodiments, the compression ratio of the respective compressor 204 is defined by the ratio of the absolute discharge pressure to the absolute suction pressure of the respective compressor 204. In other words, in some such embodiments, the compression ratio of the respective compressor 204 is the ratio of the pressure at the inlet (e.g., inlet 224) of the respective compressor 204 to the pressure at the outlet of the respective compressor 204. Thus, a higher compression ratio produces a greater pressure increase when a fluid is compressed via the respective compressor 204.

[0080] 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.

[0081] Furthermore, in some embodiments, each compressor 204 in the series of at least two compressors 204 in the 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., Fig. 9 power supply 986) and / or a corresponding variable frequency drive (VFD) controller (e.g., Fig. 9 The impeller speed (e.g., rotational speed) is associated with a controller (e.g., a controller 906) that allows the corresponding compressor 204 to be individually operated differently 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., Fig. 9 906) which controls the impeller speed via a VFD associated with the corresponding motor. For example, in some embodiments, the impeller speed is controlled individually (e.g., by Fig. 9 The controller 906 of the compressor group 202 controls the impeller speed of each compressor 204 in order to maintain a constant pressure for supplying high pressure steam 140 to the facility. However, the present disclosure is not limited thereto.

[0082] In some embodiments, the controller 906 is configured to modify the rotation speed of the corresponding compressor 204 in a series of at least two compressors 204 in the compressor group 202. For example, in some embodiments, the controller 906 is configured to modify the rotation speed of each corresponding compressor 204 in the compressor group 202, so as to maintain the pressure of the outlet of the compressor group 202, for example, so as to maintain the outlet pressure of the high-pressure steam 140 at a pressure of at least 80PSI. However, the present disclosure is not limited to this. For example, in some embodiments, the controller is configured to increase the rotation speed of the first compressor 204-1, reduce the rotation speed of the first compressor 204-1, increase the rotation speed of the second compressor 204-2, reduce the rotation speed of the second compressor 204-2, or a combination thereof (for example, reduce the rotation speed of the first compressor 204-1 and increase the rotation speed of the second compressor 204-2, etc.). However, the present disclosure is not limited to this.

[0083] In addition, the compressor unit 202 includes an inlet of the compressor unit 202 (e.g., Figures 2A to 5B The first inlet 216-1 of any one of the flasher groups 210, etc.) allows the compressor group 202 to receive a medium flow, such as low-pressure steam generated by a corresponding flasher in the flasher group 210 (e.g., by Figures 2A to 5B The first low-pressure steam 206-1 produced by the first flash evaporator 212-1 of any one of Figures 2A to 5B The second low-pressure steam 206-2 generated by the second flash evaporator 212-2 of any one of the flash evaporators, ... the low-pressure steam n 206-n generated by the flash evaporator n 212-n, etc.).

[0084] In addition, the compressor unit 202 includes an outlet of the compressor unit 202 (e.g., Figures 2A to 5B 102, and the like). In some embodiments, outlet 208 of compressor package 202 is configured to provide high pressure steam to facility 102. For example, in some embodiments, outlet 208 of compressor package 202 is configured to couple to an existing steam main of facility 102, which allows system 104 to provide high pressure steam 140 without reconfiguring facility 102, such as by requiring a new steam main at facility 102.

[0085] refer to Figures 3 to 5CIn some embodiments, three or more compressors 204 in the compressor group 202 have decreasing sizes along the forward direction extending from the inlet to the outlet of the compressor group 202. In some embodiments, in the compressor group 202, the upstream compressor is located closer to the inlet than the downstream compressor, and the size of the upstream compressor is less than or equal to the size of the downstream compressor. In some embodiments, three or more compressors 204 in the compressor group 202 have the same size along the direction extending from the inlet to the outlet of the compressor group. In some embodiments, all compressors 204 in the compressor group 202 are equal to or less than the predefined compressor size limit. In some embodiments, during the process of designing the system 104, the number of compressors 204 in the compressor group 202 is determined based on the steam parameters 116 (e.g., pressure and temperature) measured at the inlet and outlet of the compressor group 202. The size of the compressors 204 in the compressor group 202 increases along the reverse direction extending from the outlet to the inlet of the compressor group 202. In some cases, the subset of compressors 204 (e.g., 2 compressors) coupled to the inlet have the same size equal to the predefined compressor size limit. Based on a determination that subset of compressors 204 includes two or more compressors 204 , one or more flashers 212 are added to facilitate a corresponding cascade compression process implemented by compressor group 202 .

[0086] In some embodiments, the outlet of the compressor assembly 202 is configured to provide the 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 assembly 202 is configured to provide the high pressure steam 140 at a pressure 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 (3.4 4Bar) and 150PSI (10.3Bar), 50PSI (3.44Bar) and 125PSI (8.62Bar), 50PSI (3.44Bar) and 100PSI (6.89Bar), 110PSI (7.58Bar) and 315PSI (21.7Bar), 110PSI (7.58Bar) and 300PSI (20.7Bar), 110PSI (7.58Bar) and 275PSI (19.0Bar), 110PSI (7.58Bar) and 250PSI (17.2 ...315PSI (21.7Bar), 110PSI (7.58Bar) and 315PSI (21.7Bar), 110PSI (7. PSI (15.5 Bar), 110 PSI (7.58 Bar) and 200 PSI (13.8 Bar), 110 PSI (7.58 Bar) and 175 PSI (12.1 Bar), 110 PSI (7.58 Bar) and 150 PSI (10.3 Bar), 110 PSI (7.58 Bar) and 125 PSI (8.62 Bar), 170 PSI (11.7 Bar) and 315 PSI (21.7 Bar), 170 PSI (11.7 Bar) and 300 PSI (20.7 Bar) PSI (15.6 Bar) and 315 PSI (21.7 Bar), 230 PSI (15.6 Bar) and 300 PSI (20.High pressure steam 140 is provided to an existing steam main of facility 102 at a pressure between 20 PSI (15.6 Bar) and 275 PSI (19.0 Bar), between 230 PSI (15.6 Bar) and 250 PSI (17.2 Bar), between 290 PSI (20.0 Bar) and 315 PSI (21.7 Bar), or between 290 PSI (20.0 Bar) and 300 PSI (20.7 Bar), inclusive. In some embodiments, the compressor unit 202 is configured to provide high pressure steam 140 to an existing steam main of the 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), at least 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 unit 202 is configured to provide high pressure steam 140 to an existing steam main of the facility 102 at a pressure of at most 50 PSI (3.44 Bar), at most 70 PSI (4.83 Bar), at most 90 PSI (6.21 Bar), at most 110 PSI (7.58 Bar), at most 130 PSI (8.96 Bar), at most 150 PSI (10.3 Bar), at most 170 PSI (11.7 Bar), at most 190 PSI (13.1 Bar), at most 210 PSI (14.5 Bar), at most 230 PSI (15.6 Bar), at most 250 PSI (17.2 Bar), at most 270 PSI (18.6 Bar), at most 290 PSI (20.0 Bar), or at most 310 PSI (21.4 Bar). Thus, system 104 is capable of providing high pressure steam 140 to facility 102 at a pressure sufficient to enable high pressure steam 140 to be directly utilized by facility 102. In some embodiments, all pressures in this paragraph are referenced as gauge pressures. In some embodiments, unless expressly stated otherwise, all pressures in this disclosure are gauge pressures.

[0087] System 104 further includes a flasher train (e.g., Figures 2A to 5B The flasher group 210 includes a series of at least two flashers (e.g., Figures 2A to 5BThe first flash evaporator 212-1 of any one of Figures 2A to 5B The second flash evaporator 212-2 of any one of the ... Figure 5BFlash evaporator 212-n, etc.). For example, in some embodiments, the flasher bank 210 includes between two and twenty flashers 212, between two and seventeen flashers 212, between two and fifteen flashers 212, between two and twelve flashers 212, between two and nine flashers 212, between two and six flashers 212, between two and three flashers 212, between three and twenty flashers 212, between three and seventeen flashers 212, between three and fifteen flashers 212, between three and twelve flashers 212, between three and nine flashers 212, between three and six flashers 212, between five and twenty flashers 212, between five and seventeen flashers 212, between five and fifteen flashers 212, between five and twelve flashers 212, between five and nine flashers 212, and between five and six flashers 212. , between seven and twenty flash evaporators 212, between seven and seventeen flash evaporators 212, between seven and fifteen flash evaporators 212, between seven and twelve flash evaporators 212, between seven and nine flash evaporators 212, between nine and twenty flash evaporators 212, between nine and seventeen flash evaporators 212, between nine and fifteen flash evaporators 212, between nine and twelve flash evaporators 212, between eleven and twenty flash evaporators 212 2. Between eleven and seventeen flash evaporators 212, between eleven and fifteen flash evaporators 212, between eleven and twelve flash evaporators 212, between thirteen and twenty flash evaporators 212, between thirteen and seventeen flash evaporators 212, between thirteen and fifteen flash evaporators 212, between fifteen and twenty flash evaporators 212, between fifteen and seventeen flash evaporators 212, or between seventeen and twenty flash evaporators 212, including the end values. In some embodiments, the flasher group 210 includes at least two flashers 212, at least three flashers 212, at least four flashers 212, at least five flashers 212, at least six flashers 212, at least seven flashers 212, at least eight flashers 212, at least nine flashers 212, at least ten flashers 212, at least eleven flashers 212, at least twelve flashers 212, at least thirteen flashers 212, at least fourteen flashers 212, at least fifteen flashers 212, at least sixteen flashers 212, at least seventeen flashers 212, at least eighteen flashers 212, at least nineteen flashers 212, or at least twenty flashers 212.In some embodiments, the flasher group 210 includes at most two flashers 212, at most three flashers 212, at most four flashers 212, at most five flashers 212, at most six flashers 212, at most seven flashers 212, at most eight flashers 212, at most nine flashers 212, at most ten flashers 212, at most eleven flashers 212, at most twelve flashers 212, at most thirteen flashers 212, at most fourteen flashers 212, at most fifteen flashers 212, at most sixteen flashers 212, at most seventeen flashers 212, at most eighteen flashers 212, at most nineteen flashers 212, or at most twenty flashers 212. However, the present disclosure is not limited thereto. For example, briefly refer to. Figure 5C In some embodiments, the flasher group 210 includes one flasher 212 as the terminal flasher 212. In some embodiments, the flasher group 210 consists of one flasher 212.

[0088] In some embodiments, each compressor 204 in the compressor train 202 and each flasher 212 in the flasher train 210 share a one-to-one relationship. Figure 2A , the system 104 depicts a one-to-one relationship between each compressor 204 in the compressor group 202 and each flasher 212 in the flasher group 210, because the compressor group 202 has two compressors 204, and the flasher group 210 similarly has two flashers 212. In some embodiments, the compressor 204 and the flasher 212 share a one-to-one relationship when the temperature difference between the first compressor and the second compressor meets a threshold temperature, such as 10° C., 20° C., etc. In some embodiments, the compressor 204 and the flasher 212 share a one-to-one relationship when the temperature difference between the first flasher and the second flasher meets a threshold temperature, such as 20° C. Thus, in some embodiments, the compressor group 202 includes p compressors (e.g., a first compressor 204-1, a second compressor 204-2, ... compressor p 204-p), and the flasher group 210 includes p flashers 212 (e.g., a first flasher 212-1, a second flasher 212-2, ... flasher p 212-p), where p is an integer that is (i) greater than or equal to two and (ii) less than or equal to twenty. In some embodiments, p is an integer that is (i) greater than two and (ii) less than or equal to twenty. However, the present disclosure is not limited thereto. In some embodiments, each compressor 204 in the compressor group 202 and each flasher 212 in the flasher group 210 share a many-to-one relationship. As another non-limiting example, briefly refer to Figure 4, the system 104 depicts a many-to-one relationship for each compressor 204 in the compressor train 202 and each flasher 212 in the flasher train 210 because the compressor train 202 has three compressors 204 and the flasher train 210 has two flashers 212. For example, in some embodiments, when the first size of the first compressor 204 is the same as the second size of the second compressor 204, then the first flasher 212 is disposed between the first compressor 204 and the second compressor 204, which results in a many-to-one relationship. Therefore, in some embodiments, the compressor group 202 includes m compressors 204 (e.g., a first compressor 204-1, a second compressor 204-2, ... compressor m 204-m), and the flasher group 210 includes n flashers 212 (e.g., a first flasher 212-1, a second flasher 212-2, ... flasher n212-n), where m and n are each an integer that is (i) greater than or equal to two and (ii) less than or equal to twenty, and m is greater than n.

[0089] Similar to the series of at least two compressors 204 in the compressor train 202, the series of at least two flashers 212 in the flasher train 210 are at least partially fluidly coupled in series, which allows the medium flow to flow from one flasher 212 in the series of at least two flashers 212 to another flasher 212 in the series of at least two flashers. For example, in some embodiments, briefly refer to Figure 2A , when the series of at least two flashers 212 are at least partially fluidly coupled in series, the series of at least two flashers 212 includes a trace through both the second inlet 224-2 of the second flasher 212-2 in the flasher group 210, the second liquid outlet 228-2 of the second flasher, and the first inlet 224-1 of the first flasher 212-1.

[0090] Thus, a series of at least two flashers 212 includes a terminal flasher 212 at one end of the flasher train 210. For example, referring briefly to Figure 2A , the first flasher 212-1 is a first terminal flasher 212 at one end of the flasher group 210 in a series of at least two flashers 212, and the second flasher 212-2 is a second terminal flasher 212 at a second end of the flasher group 210 in a series of at least two flashers 212. As another non-limiting example, briefly refer to Figure 5A , the first flasher 212-1 is a first terminal flasher 212 at one end of the flasher group 210 in a series of at least two flashers 212, and the flasher 212-n is a second terminal flasher 212 at a second end of the flasher group 210 in a series of at least two flashers 212. Therefore, by fluidly connecting at least two flashers 212 in series, the flasher group 210 is able to utilize condensed water from steam (e.g., Figures 2A to 5B The heat energy of any one of the steam condensation water reflux 214, etc. However, the present disclosure is not limited thereto.

[0091] In some embodiments, each flasher 212 in the series of at least two flashers 212 is configured to maintain (e.g., by Fig. 9 The control module 906 of the system 104 is configured to maintain the hot water received from the inlet 224 at a predetermined internal pressure or a predetermined internal pressure range that is less than the saturation pressure of the hot water received from the system 104. For example, in some embodiments, each flasher 212 is configured to maintain an internal pressure that is less than the saturation pressure of the hot water received from the inlet 224 into the corresponding flasher 212. In addition, each flasher 212 in the series of at least two flashers 212 is configured to expand the hot water received from the inlet 224 of the flasher 212 to produce low-pressure steam (e.g., Figures 2A to 5B The first low-pressure steam 206-1 produced by the first flash evaporator 212-1 of any one of Figures 2A to 5B , ..., low-pressure steam n 206-n generated by flasher n 212-n, etc.). For example, in some embodiments, the internal pressure of a corresponding flasher 212 in the flasher group 210 is based on the first temperature of the hot water received by the system 104 or the condensed water received by the corresponding flasher 212 (e.g., Figure 4 Steam condensate reflux 214, Figure 2A As a non-limiting example, in some embodiments, the hot water source 110 provides hot water having a temperature of 120°F, and then the terminal flasher 212-1 in the flasher group 210 is configured to have an internal pressure of about 88 millibars absolute (mBara), which is the saturation pressure of water at 110°F. However, the present disclosure is not limited thereto. In some embodiments, the internal pressure of the corresponding flasher 212 is less than the saturation temperature of the medium received by the flasher, such as the liquid received from the liquid outlet 228 of the adjacent flasher 212 or the hot water received from the hot water source 110. Therefore, by configuring each flasher 212 in a series of at least two flashers 212 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, the system 104 is not only able to be connected to various facilities 303 having different hot water source 110 temperatures, but also can actually adapt to changes in operating parameters 916 at the corresponding facilities 102 connected to the system 104.

[0092] In some embodiments, one or more flashers 212 in the flasher group 210 are positioned at the inlet of the flasher group 210 (eg, Figures 2A to 5BThe system 104 is configured to be above the second inlet 224-2 of any one of the flashers 210, etc.), so that each of the one or more flashers 212 is elevated or substantially elevated from the inlet 224-2 of the flasher group 210, which effectively increases the potential energy of each of the one or more flashers 212. By placing the one or more flashers 212 in the flasher group 210 above the inlet 224-2 of the flasher group 210, the system 104 is configured to utilize the additional potential energy obtained from the pressure difference between the inlet 224-2 of the flasher group 210 and the height of the one or more flashers 212 in the flasher group 210. In addition, when receiving the cooled water generated by each of the one or more flashers 212 in the flasher group 210, such a configuration allows the system 104 to have minimal power consumption (e.g., by Fig. 9 Operation Figure 2A The electrical power consumed by the power supply 986 required for the re-boosting pump 220).

[0093] Thus, in some embodiments, each flasher 212 in the series of at least two flashers 212 includes two or more outlets. For example, in some embodiments, the vapor outlet (e.g., Figures 2A to 5B The vapor outlet 226-1 of the flash evaporator 212-1 of any one of Figures 2A to 5B The vapor outlet 226-2 of the flash evaporator 212-2 of any one of Figure 5A The vapor outlet 226-n of the flasher 212-n of the terminal flasher 212-n, etc.) is configured to deliver the low-pressure steam 206 generated by the flasher 212 to the compressor 204 in the compressor train 202. For example, in some embodiments, the first vapor outlet 226-1 of the terminal flasher 212-1 is fluidly coupled to the inlet 216-1 of the compressor train 202.

[0094] In addition, the system 104 includes a vapor outlet 226 of the remainder of the series of at least two flashers 212, which is fluidly coupled between the compressors 204 in the series of at least two compressors 204 in the compressor train 202. As a non-limiting example, briefly refer to Figure 2A and Figure 4 , the second vapor outlet 226-2 of the second flasher 212-2 is fluidly coupled to the second inlet 216-2 of the second compressor 204-2 in the compressor train 202. As yet another non-limiting example, briefly refer to Figure 3 The second vapor outlet 226 - 2 of the second flasher 212 - 2 is fluidly coupled to the third inlet 216 - 3 of the third compressor 204 - 3 in the compressor train 202 .

[0095] In some embodiments, the flasher group 210 further comprises an inlet of the flasher group 210 (e.g., Figure 5AThe inlet 224 of the flasher bank 210 is configured to receive hot water from a facility 102 (e.g., the hot water source 110 of any of FIGS. 1 to 5 , etc.). For example, in some embodiments, the inlet 224 of the flasher bank 210 is configured to receive hot water from the same facility 102 that provides the high pressure steam 140 thereto (e.g., the hot water source 110 of any of FIGS. 1 to 5 ). Figure 1B hot water received from a hot water source 110 of a first facility 102-1) or received from a hot water source 110 of a different facility 102 (e.g., Figure 1A In some embodiments, the hot water received from the hot water source 110 of the second facility 102-2 is provided. In some embodiments, the different facilities 102 that provide the hot water received from the hot water source 110 are not associated with the utilization of the high-pressure steam 140 generated by the system 104. However, the present disclosure is not limited thereto. In addition, in some such embodiments, by utilizing hot water as a medium flowing through the system 104 (e.g., as a refrigerant for the system 104), the efficiency of the system 104 is improved because water has zero global warming potential (0 GWP), is non-flammable and non-toxic, and has no regulatory risk compared to other conventional refrigerants such as hydrofluorocarbons (HFCs) and / or hydrofluoroolefins (HFOs) that are toxic and / or flammable.

[0096] In some embodiments, the inlet 224 of the flasher group 210 is the inlet of the terminal flasher 212-1 in the flasher group 210. For example, in some embodiments, the second inlet 224-2 of the terminal flasher 212-1 is configured to receive hot water received from the hot water source 110, and the hot water is supplied to the interior of the terminal flasher 212-1.

[0097] In some embodiments, the remaining portions of the series of at least two flashers 212 each include a liquid outlet (e.g., the second liquid outlet 228-2 of any of Figures 2 to 5, etc.). Each liquid outlet 228 of each of the remaining portions of the series of at least two flashers 212 is fluidly coupled to an inlet 224 of another of the series of at least two flashers 212. As a non-limiting example, briefly refer to Figure 2A , the second flasher 212-2 belongs to the rest of the series of at least two flashers 212, because the second flasher 212-2 is not the end flasher 212-1 in the flasher group 210, and the second flasher 212-2 includes a second liquid outlet 228-2 fluidly coupled to the inlet 224-1 of the end flasher 212-1 in the series of at least two flashers 212.

[0098] In some embodiments, the end flasher 212-1 includes a liquid outlet (e.g., the first liquid outlet 228-1 of any of FIGS. 2 to 5, etc.) fluidly coupled to an outlet of the system 104. As a non-limiting example, in some embodiments, the outlet of the system 104 is a cooling water source associated with the first facility 102-1 that receives the high pressure steam 140 generated by the system 104 or the second facility 102-2 associated with the hot water received by the system 104 from the hot water source 110 (e.g., FIGS. 1 to 5). Figure 7 102, or a cooling water source 120 of any of the above). 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 a different facility 102. In this way, in some such embodiments, the outlet of the cooling water source 120 of the system 104 is configured as a cooling water source for a closed-loop cooling water process associated with the facility providing the hot water source 110. Furthermore, in some embodiments, by connecting the system 104 only to the existing steam main and cooling water source 120 of the same facility 102, the system 104 does not require extensive modification in order to perform under the unique operating conditions of the corresponding facility 102.

[0099] In some embodiments, the liquid outlet 228-1 of the end flasher 212-1 is fluidly coupled to a re-boosting pump (e.g., the re-boosting pump 220 of any one of FIGS. 2 to 5 , etc.). The re-boosting pump 220 is coupled to the outlet of the cooling water source 120 of the system 104 so as to be interposed between the liquid outlet 228 of the end flasher 212-1, which allows the re-boosting pump 220 to deliver the fluid generated by the end flasher 212-1 to the outlet of the cooling water source 120 when there is a pressure gradient between the pressure of the fluid generated by the end flasher 212-1 and the outlet of the cooling water source 120 of the system 104. For example, in some embodiments, the re-boosting pump 220 is configured to generate a negative pressure gradient so as to receive the cooled water generated by the flasher 212 from the liquid outlet 228 of the flasher 212, for example, so as to maintain a steady state of the flasher 212. However, the present disclosure is not limited thereto. In some embodiments, the re-boost pump 220 is configured to maintain the pressure of the liquid outlet 228 of the flasher 212 at a predetermined pressure or a predetermined pressure range.

[0100] In some embodiments, the system 104 includes one or more valves (eg, the first valve 218-1, Figures 2A to 5B The second valve 218-2 of any one of Figure 5A The third valve 218-3, Figure 5A The fourth valve 218-4, ... Figure 5A218-n, etc.), wherein each valve 218 of the one or more valves 218 is configured to control (e.g., block and / or delay) the flow of a medium (e.g., the flow rate of hot water received from the hot water source 110, the flow rate of the low-pressure steam 206, the flow rate of cooling water, etc.) through the valve 218, wherein the flow is ultimately received by or from the corresponding flasher 212. In some embodiments, the valve 218 of the one or more valves 218 is disposed at the inlet of the corresponding flasher 212 (e.g., Figure 5A The first entrance 224-1, Figure 5A 224-2, etc.) or downstream of an outlet of the corresponding flash evaporator 212, such as a vapor outlet 226 or a liquid outlet 228. In some embodiments, each valve 218 is configured to meter a flow rate of a medium received by or from the corresponding flash evaporator 212 (e.g., a flow rate of hot water received from the hot water source 110, a flow rate of the low-pressure steam 206, a flow rate of cooled water, etc.).

[0101] In some embodiments, the system 104 further includes a controller (e.g., Fig. 9 In some embodiments, the controller 906 is configured to maintain a temperature range for the flasher bank 210, such as maintaining a temperature of the high pressure steam 140 generated by the system 104 and / or a temperature of an outlet of the system 104, such as a temperature of the cooling water source 120 associated with the facility 102.

[0102] In some embodiments, the controller 906 is configured to maintain the respective centrifugal compressors 204 in the compressor train 202 from blocking or surging. For example, in some embodiments, the controller 906 is configured to determine whether the mass flow rate associated with the respective centrifugal compressors 204 in the compressor train 202 satisfies a first threshold mass flow rate associated with a blocking condition of flow within the respective centrifugal compressors 204 and / or a second threshold mass flow rate associated with a surge condition of flow within the respective centrifugal compressors 204. However, the present disclosure is not limited thereto. As a non-limiting example, each respective compressor 204 has a minimum mass flow rate at which the respective compressor 204 can stably operate, which is a surge condition.

[0103] In some embodiments, the system 104 further comprises a desuperheater group (e.g., Figure 5A In some embodiments, the desuperheater group 230 includes at least one desuperheater (e.g., Figure 5AFor example, in some embodiments, the desuperheater group 230 includes between two and twenty desuperheaters 232, between two and seventeen desuperheaters 232, between two and fifteen desuperheaters 232, between two and twelve desuperheaters 232, between two and nine desuperheaters 232, between two and six desuperheaters 232, between two and three desuperheaters 232, between three and twenty desuperheaters 232, between three and seventeen desuperheaters 232, and between two and seventeen desuperheaters. 232, desuperheaters 232 between three and fifteen, desuperheaters 232 between three and twelve, desuperheaters 232 between three and nine, desuperheaters 232 between three and six, desuperheaters 232 between five and twenty, desuperheaters 232 between five and seventeen, desuperheaters 232 between five and fifteen, desuperheaters 232 between five and twelve, desuperheaters 232 between five and nine, desuperheaters 232 between five and six , between seven and twenty desuperheaters 232, between seven and seventeen desuperheaters 232, between seven and fifteen desuperheaters 232, between seven and twelve desuperheaters 232, between seven and nine desuperheaters 232, between nine and twenty desuperheaters 232, between nine and seventeen desuperheaters 232, between nine and fifteen desuperheaters 232, between nine and twelve desuperheaters 232, between eleven and twenty desuperheaters 232 2. Between eleven and seventeen desuperheaters 232, between eleven and fifteen desuperheaters 232, between eleven and twelve desuperheaters 232, between thirteen and twenty desuperheaters 232, between thirteen and seventeen desuperheaters 232, between thirteen and fifteen desuperheaters 232, between fifteen and twenty desuperheaters 232, between fifteen and seventeen desuperheaters 232, or between seventeen and twenty desuperheaters 232, inclusive. In some embodiments, the desuperheater group 230 includes at least two desuperheaters 232, at least three desuperheaters 232, at least four desuperheaters 232, at least five desuperheaters 232, at least six desuperheaters 232, at least seven desuperheaters 232, at least eight desuperheaters 232, at least nine desuperheaters 232, at least ten desuperheaters 232, at least eleven desuperheaters 232, at least twelve desuperheaters 232, at least thirteen desuperheaters 232, at least fourteen desuperheaters 232, at least fifteen desuperheaters 232, at least sixteen desuperheaters 232, at least seventeen desuperheaters 232, at least eighteen desuperheaters 232, at least nineteen desuperheaters 232, or at least twenty desuperheaters 232.In some embodiments, the desuperheater group 230 includes at most two desuperheaters 232, at most three desuperheaters 232, at most four desuperheaters 232, at most five desuperheaters 232, at most six desuperheaters 232, at most seven desuperheaters 232, at most eight desuperheaters 232, at most nine desuperheaters 232, at most ten desuperheaters 232, at most eleven desuperheaters 232, at most twelve desuperheaters 232, at most thirteen desuperheaters 232, at most fourteen desuperheaters 232, at most fifteen desuperheaters 232, at most sixteen desuperheaters 232, at most seventeen desuperheaters 232, at most eighteen desuperheaters 232, at most nineteen desuperheaters 232 or at most twenty desuperheaters 232.

[0104] Each desuperheater 232 in the desuperheater group 230 includes an outlet configured to inject hot water received from the facility 102 or a different facility 102 into the compressor group 202. For example, in some embodiments, each desuperheater 232 in the desuperheater group 230 is configured to receive a portion of the hot water received from the hot water source 110 that is supplied to the inlet 224-2 of the terminal flasher 212-1, which allows the desuperheater group 230 to utilize the same source of hot water received from the hot water source 110. However, the present disclosure is not limited thereto. In some embodiments, each desuperheater 232 in the desuperheater group 230 is configured to remove heat (e.g., superheat) added to the low-pressure steam 206 by each compressor 204 in the compressor group 202 by injecting the hot water received from the hot water source 110 into the low-pressure steam 206 between the compressors 204. Thus, in some such embodiments, the water injected by the desuperheater 232 evaporates, which removes superheat from the low-pressure steam 206 and increases the mass flow of the low-pressure steam 206 through the system 104. In some embodiments, the desuperheater group 230 is configured such that each compressor 204 in the compressor group 202 does not require an interstage cooler. Furthermore, in some embodiments, the high efficiency of the system 104 is achieved by utilizing the desuperheater group 230 to provide desuperheating of the low-pressure steam 206 as the low-pressure steam 206 is compressed by the compressor 204, which allows the system 104 to operate at or approximately at the water saturation line without heat losses that would otherwise be incurred by an intercooler or entropy losses due to a large amount of superheating.

[0105] In some embodiments, each compressor 204 in the compressor group 202 and each desuperheater 232 in the desuperheater group 230 share a one-to-one relationship. Figure 5A, the system 104 depicts a one-to-one relationship between each compressor 204 in the compressor group 202 and each desuperheater 232 in the desuperheater group 230, because the compressor group 202 has four compressors 204, and the desuperheater group 230 similarly has four desuperheaters 232. Therefore, in some embodiments, the compressor group 202 includes m compressors (e.g., Figure 5A The first compressor 204-1, the second compressor 204-2, ..., the compressor m204-m), and the desuperheater group 230 includes q desuperheaters 232 (for example, Figure 5A The first desuperheater 232-1, the second desuperheater 232-2, ... desuperheater q 232-q), wherein m and q are the same integer (i) greater than or equal to two and (ii) less than or equal to twenty. In some embodiments, m and q are the same integer (i) greater than two and (ii) less than or equal to twenty. However, the present disclosure is not limited to this. In some embodiments, each compressor 204 in the compressor group 202 and each desuperheater 232 in the desuperheater group 230 share a many-to-one relationship. Therefore, in some such embodiments, the compressor group 202 includes m compressors, and the desuperheater group 230 includes q desuperheaters 232, wherein m and q are each an integer (i) greater than or equal to two and (ii) less than or equal to twenty, and m is greater than q. However, the present disclosure is not limited to this.

[0106] In some embodiments, the system 104 includes a coefficient of performance (COP) greater than 65% of the corresponding Carnot efficiency, where the Carnot efficiency represents the highest possible efficiency of a heat pump system operating between a higher temperature source and a lower temperature source. For example, in some embodiments, the system 104 as a heat pump system 104 operating between two sources of different thermal temperatures (e.g., a higher temperature hot water source 110 and a lower temperature cooling water source 120, a lower temperature hot water source 110 and a higher temperature high pressure steam, a higher temperature high pressure steam and a lower temperature cooling water source 120, or a combination thereof) has an associated efficiency rating, which is determined based on a coefficient of performance (COP), an energy efficiency ratio (EER), etc. In some embodiments, the COP is determined based on the value of the heat transferred from the lower temperature source divided by the network input, which is the value of the heat transferred to the higher temperature source minus the refrigerant effect value. For example, in some embodiments, the COP of the system 104 is determined based on the temperature of the high pressure steam 140 generated by the system 104 and the temperature of the hot water source 110 that provides the hot water received by the system. In some embodiments, the COP of the system 104 is determined based on the ratio of the electrical power consumption of the system 104 to the output thermal power of the system 104. In some embodiments, the corresponding Carnot efficiency percentage is determined based on the ratio of the Carnot COP to the actual COP of the system 104. Additional details and information about the COP and / or Carnot efficiency of heat pump systems are found in Sadegh et al., 2018, "Marks' Standard Handbook for Mechanical Engineers", McGraw-Hill Education., print, which is hereby incorporated by reference in its entirety for all purposes.

[0107] In some embodiments, the flasher 212 in the flasher train 210 includes a blowdown device (e.g., Figure 1A or Figure 5B170, etc.). In some embodiments, the blowdown member 170 is configured to remove contaminants contained by the flasher 212. For example, in some embodiments, the blowdown member 170 is configured to continuously remove contaminants contained by the flasher 212 (e.g., continuous blowdown member 170) or intermittently remove contaminants contained by the flasher 212. For example, in some embodiments, the contaminants include one or more fluids and / or one or more solids, which are at least partially removed from the system 104 by discharging the contaminants through the blowdown member 170, which allows downstream components of the system 104 and the flasher 212 to remain unhindered in terms of heat transfer efficiency by the contaminants. In some embodiments, the contaminants are free of or substantially free of steam (e.g., low pressure steam 206, high pressure steam 140, etc.). In some embodiments, by purging the contaminants through the blowdown member 170, the flasher 212 is allowed to further receive hot water received from the hot water source 110, and thus generate high pressure steam 140 via the compressor unit 202, such as supplemental hot water received from the hot water source 110. In addition, in some embodiments, the blowdown member 170 is configured to at least partially remove the contaminants at a temperature below the first temperature of the hot water, which allows the purge to be completed without causing heat loss to the system 104. However, the present disclosure is not limited in this regard. In some embodiments, the blowdown member 170 is configured to continuously remove the contaminants without an active control mechanism (e.g., without receiving one or more instructions from the controller 906). For example, in some embodiments, the blowdown member 170 is electronically connected to a sensor 982 that is configured to detect one or more contaminants within the flasher 212, such as a conductivity sensor 982, which provides feedback information to the blowdown member 170 regarding the status of the one or more contaminants.

[0108] In some embodiments, the blowdown 170 is associated with the second liquid outlet of a corresponding flasher 212 in the flasher bank 210. In some embodiments, the blowdown 170 is fluidly configured to selectively remove fluid from the corresponding flasher 212.

[0109] In some embodiments, the controller 906 is in electronic communication with the second liquid outlet of the corresponding flasher 212. In some embodiments, the controller is configured to control the selective removal of the fluid.

[0110] In some embodiments, the flasher 212 in the flasher train 210 includes a degasser (e.g., Figure 5BIn some embodiments, the degasser 240 is configured to form an outlet of the flasher 212, such as a second liquid outlet of the flasher 212. In some embodiments, the degasser 240 is configured to selectively remove fluid from the corresponding flasher 412. For example, in some embodiments, based on the determination of a threshold amount of the first medium (e.g., contaminants in the flasher, hot water in the flasher, steam in the flasher, etc.), the degasser 240 is configured to modify the opening of the outlet of the flasher 212, which allows the fluid to be selectively removed from the corresponding flasher 212. In some such embodiments, the fluid removed from the corresponding flasher 212 includes one or more gases (e.g., oxygen, carbon dioxide, etc.) contained by the flasher 212 and / or one or more liquids contained by the flasher 212. However, the present disclosure is not limited thereto. In some embodiments, the controller 906 of the system 104 is electronically connected to the second liquid outlet associated with the degasser 240. In some such embodiments, the controller 906 is configured to selectively allow fluid communication between the second liquid outlet and the outlet of the system 104, which allows fluid to be removed from the flasher 212. In some embodiments, based on a determination that the temperature and / or pressure associated with the compressor group 202 meets a threshold pressure and / or temperature, the controller 906 is a controller configured to modify the flow rate of the fluid through the desuperheater 232. As a non-limiting example, in some embodiments, the controller 906 is configured to modify the size of the second outlet, such as the diameter of the orifice or opening of the outlet of the desuperheater 232. For example, in some embodiments, based on a determination that the pressure associated with the compressor 204 is less than the threshold pressure and therefore does not meet the threshold pressure, the controller is configured to reduce the size of the second outlet (e.g., the diameter of the orifice) so as to increase the internal pressure of the system 104 and / or so as to modify the mass flow rate of the fluid output by the desuperheater 232. However, the present disclosure is not limited thereto.

[0111] In some embodiments, the system 104 further comprises one or more boilers (e.g., Figure 5A The boiler 236 is arranged to be inserted between the outlets 208 of the compressor group 202 and fluidly coupled to the outlets 208 of the compressor group 202. In some embodiments, the boiler 236 is configured to remove moisture or condensate from the high pressure steam 140 generated by the compressor group 202. For example, in some embodiments, the boiler 236 is configured to heat the high pressure steam, for example, to produce superheated steam. In some embodiments, the boiler 236 is configured to provide supplemental steam to address peak steam demand from the facility 102 that exceeds the steam generation capacity of the compressor group 202. In some embodiments, the boiler 236 is configured to serve as a backup source of steam generation for the facility 102 in the event that the compressor group 202 is intentionally or unintentionally powered off. However, the present disclosure is not limited thereto.

[0112] In some embodiments, the system 104 further comprises a steam accumulator (e.g., Figure 5A The steam accumulator 238 is disposed to be interposed between and fluidly coupled to the outlet 208 of the compressor group 202. For example, in some embodiments, the steam accumulator 238 is configured to increase the storage capacity of the system 104, which allows the system 104 to respond to fluctuations (e.g., one or more peaks and / or one or more valleys) in the facility's demand for the high-pressure steam 140 generated by the system 104.

[0113] The systems, methods, and apparatus of the present disclosure have other features and advantages that will be apparent from or set forth in more detail in the accompanying drawings and the following detailed description incorporated herein, which together serve to explain certain principles of the invention.

[0114] Figure 6 is a graph depicting various parameters associated with various high pressure steam generating heat pump systems according to some embodiments. Figure 6 In some embodiments, the systems, methods, and apparatus of the present disclosure provide a plurality of heat pump systems 104. In some embodiments, each heat pump system 104 in the plurality of heat pump systems 104 is configured to achieve a unique set of parameter requirements. In some embodiments, the parameters (e.g., Fig. 9 The unique set of parameters 916 required by the heat pump system 104 includes the output pressure of the high pressure steam generated by the corresponding system 104, the output flow rate of the high pressure steam generated by the corresponding system 104, and the temperature of the hot water source 110 received by the corresponding system 104. In some embodiments, the remainder of the parameters 916 remain constant on each heat pump system 104, or are derived directly from the unique set of parameters 916 associated with the corresponding system 104.

[0115] In addition, the systems, methods, and apparatus of the present disclosure avoid intermediate refrigerants and the associated losses of transferring heat to and / or from the intermediate refrigerants. Specifically, the systems, methods, and apparatus of the present disclosure generate high pressure steam directly from the hot water source 110 and directly compress it together with the low pressure steam generated by the flasher group 210 using a multi-stage mechanical vapor recompression (MVR) compressor group 202 having a series of at least two centrifugal compressors 204. In some embodiments, the system 104 includes a desuperheater group 230, which includes a desuperheater 232 disposed between each compressor 204 in the compressor group 202.

[0116] Thus, in some embodiments, the systems, methods, and apparatus of the present disclosure achieve high COP (e.g., COP of 4.5, COP of 4.0, etc.) by utilizing the high efficiencies associated with utilizing one or more centrifugal compressors 204 in the compressor train 202 and avoiding superheat losses associated with high compression ratio compressors 204 typically found in conventional high temperature industrial heat pump technology.

[0117] Figure 7 Graph depicting the performance of a high pressure steam generating heat pump system according to some embodiments compared to various conventional technologies. In some embodiments, the heat pump system 104 of the systems, methods, and apparatus of the present disclosure is used to generate high pressure steam 140 as a comparison to conventional high temperature industrial heat pump technology. The heat pump system 104 performs better than conventional high temperature industrial heat pumps.

[0118] In some embodiments, the primary competitive advantage of the systems, methods, and apparatus of the present disclosure over conventional high temperature industrial heat pump technology is the ability to produce steam at higher pressures, produce high pressure steam with a higher coefficient of performance, use a more attractive refrigerant in the form of water, or a combination thereof.

[0119] 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 generates thermal energy at temperatures up to 320 degrees Fahrenheit (160°C). In some embodiments, conventional high temperature industrial heat pumps are not able to directly generate steam, but must be used in combination with an unfired steam generator, which introduces a nominal temperature drop of 20°F. Therefore, the maximum saturated steam pressure that a conventional high temperature industrial heat pump can produce is 3.5 Barg (50 PSIg), which is insufficient to address the medium pressure (e.g., between 3.5 Barg and 20 Barg) applications common to industrial facilities 102. In addition, conventional high temperature industrial heat pumps have a relatively low coefficient of performance of less than 3.0, resulting in high electricity demand and high operating costs.

[0120] In addition, one or more HFC refrigerants have high global warming potential (GWP). In contrast, one or more HFO refrigerants have low GWP but are too expensive. In contrast, the heat pump system 104 of the system, method and apparatus of the present disclosure directly produces high-pressure steam 140 at a pressure of up to 20 Barg (290 PSIg). In addition, when performed under the same operating conditions, the heat pump system 104 of the system, method and apparatus of the present disclosure produces this high-pressure steam 140 with a COP 50% higher than that of conventional high-temperature industrial heat pumps, which results in a proportional reduction in the power demand and operating cost of the heat pump system 104 of the system, method and apparatus of the present disclosure. In addition, since the heat pump system 104 of the system, method and apparatus of the present disclosure uses water as a refrigerant, the heat pump system 104 provides the benefits of low cost, safety, non-toxicity, zero GWP or a combination thereof.

[0121] In addition, conventional high temperature industrial heat pumps based on CO2 utilize low cost and low GWP refrigerants in the form of CO2. However, due to the high pressure required for the refrigerant, conventional high temperature industrial CO2 heat pumps are limited to temperatures of 238°F (114°C) or lower. In this manner, those skilled in the art will appreciate that, although 238°F (114°C) is above the atmospheric boiling point of water, conventional high temperature industrial CO2-based heat pumps are unable to produce sufficient high pressure steam because conventional high temperature industrial CO2-based heat pumps require a low fluid return temperature of 203°F (95°C) or lower, which directly determines the ability of conventional high temperature industrial CO2-based heat pumps to drive steam generators.

[0122] Furthermore, conventional high temperature industrial heat pumps, which are ammonia based heat pumps, have high pressure characteristics, which limit conventional high temperature industrial ammonia based heat pumps to a maximum output temperature of 203° F. (95° C.), which is not suitable for steam generation.

[0123] refer to Figure 7 In some embodiments, the heat pump system 104 of the systems, methods, and apparatus of the present disclosure is used to generate high pressure steam 140 as a comparison to conventional boiler technology (eg, conventional electric boiler technology and / or conventional natural gas boiler technology). The heat pump system 104 performs better than conventional boilers.

[0124] In some embodiments, the main competitive advantage of the systems, methods and apparatus of the present disclosure over conventional electric boiler technology is the higher COP of the systems, methods and apparatus of the present disclosure, which results in lower operating costs. In addition, conventional electric boiler technology is determined to have a COP close to 1.0 and requires approximately 295 kilowatt-hours (kWh) of electricity to produce 1 klb of steam. When the price of industrial electricity is assumed to be $0.12 per kWh, the energy cost per klb of steam produced by the conventional electric boiler technology is $35.40.

[0125] In contrast, even though the COP of the system, method, and apparatus of the present disclosure depends 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 the common operating conditions of obtaining 85°F hot water from the facility and producing 10 Barg (130 PSIg) high pressure steam 140. Under these operating conditions, the system, method, and apparatus of the present disclosure has a COP of 3.0. In addition, the system, method, and apparatus of the present disclosure requires three times less electricity per klb of high pressure steam than a conventional electric boiler, 97 kWh. In addition, the system, method, and apparatus of the present disclosure provide three times lower energy costs than conventional electric boilers, with a cost of $11.80 per klb of high pressure steam.

[0126] In addition, the operating costs of the systems, methods, and apparatus of the present disclosure are comparable to or lower than conventional natural gas boiler technology. For example, new conventional natural gas boiler technology with economizers has a COP of 0.85 and requires approximately 11.8 thm of natural gas to produce 1 klb of high pressure steam. At a natural gas price of $1.30 / thm, conventional natural gas boiler technology requires an energy cost of $15.34 per klb of steam, which is greater than the $11.80 / klb achieved by the systems, methods, and apparatus of the present disclosure.

[0127] Figure 8 800 is a flowchart of an example method (e.g., method 800) for generating high pressure steam according to some embodiments, wherein the dashed boxes represent optional elements in the flowchart. Specifically, method 800 is applied to generate high pressure steam (e.g., Figure 1A High pressure steam 140-1 or 140-2, FIG. 1 to Figure 7 Unless otherwise explicitly stated, various modules in the memory 992 of the computer system 900 perform certain processes of the method 200 described in FIG. 2 . In addition, it will be understood that Figure 8 The processes in may be encoded in a single module or in any combination of modules.

[0128] In some embodiments, method 800 is performed from FIG. 1 to Figure 7 In some embodiments, the method 800 is performed on a computer system (e.g., Fig. 9 The computer system 900 includes one or more processors (e.g., Fig. 9 972) and a memory coupled to one or more processors 172 (e.g., Fig. 9 Memory 992). Memory 992 contains one or more programs configured to be executed by one or more processors 972 (e.g., Fig. 9 The control module 906, Fig. 9 In other words, in some embodiments, method 800 cannot be mentally performed because the computational complexity addressed by method 800 requires the use of computer system 900.

[0129] refer to Figure 8 In block 804, method 800 includes providing a heat pump system (e.g., Figures 1A to 7 104, etc.) coupled to one or more facilities (e.g., Figure 1A The first facility 102-1, Figure 1A In some cases, the heat pump system is connected to one or more facilities. In some embodiments, each facility 102 is associated with an industrial process, such as a chemical process, a pulp 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 exist within the field of the facilities 102 of the present disclosure. Therefore, the method 800 allows the heat pump system 104 to be connected to one or more facilities 102 to provide energy needs for one or more facilities 102.

[0130] In some embodiments, the heat pump system 104 is connected to a hot water source (e.g., FIG. 1 , FIG. 5 , and Figure 6 In some embodiments, the hot water source 110 is configured to capture waste heat from the first facility 102-1, which allows the heat pump system 104 to utilize this waste heat via a heat transfer process. As a non-limiting example, in some embodiments, the hot water source 110 includes boiler feed water (e.g., Figure 1A 104 ) having a high temperature where waste heat will be captured by the system 104. For example, in some embodiments, the hot water source 110 includes a cooling water stream returning from a cooling process performed at the facility 102 and / or a make-up water stream generated at the facility 102. In some embodiments, the cooling water stream returning from the cooling process performed at the facility 102 and / or the make-up water stream generated at the facility 102 are combined prior to being received by the system 104. However, the present disclosure is not limited in this regard. In some embodiments, additional hot water (e.g., boiler feed water) is received by the system 104, for example, in order to maintain a constant water volume in the system 104. However, the present disclosure is not limited in this regard. Thus, the hot water source 110 provides a low-grade heat source in the form of hot water received by the system 104, which has energy in the form of heat that the facility 102 would otherwise reject (e.g., rejecting heat to the atmosphere and / or to wastewater via a cooling tower process). Additionally, in some embodiments, the heat pump system 104 is further coupled to the same facility 102 (e.g., Figure 1A1) or a different facility 102 (e.g., Figure 1A The heat pump system 104 may be connected to an existing steam main of a second facility 102-2), which allows the heat pump system 104 to have a one-to-one relationship with a 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 of the first facility 102-1 and an existing steam main of the first facility 102-1, which allows the heat pump system 104 to generate high-pressure steam 140 that is then utilized at the first facility 102-1, the high-pressure steam being received from the hot water source 110 that captures waste heat of 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 of the first facility 102-1 and the existing steam main of the second facility 102-2, which allows the heat pump system 104 to generate high-pressure steam 140 that can be utilized at the second facility 102-2, the high-pressure steam being received from the hot water source 110 that captures waste heat of the first facility 102-1. Thus, by connecting the heat pump system 104 between the hot water source 110 of the facility 102 and the existing steam main of the same or different facility 102, the method 800 provides for optimizing the efficiency of the heat pump system 104 without modifying or substantially modifying the existing structure of the same or different facility 102 connected to the heat pump system 104, such as the existing steam main. In this way, the heat pump system 104 allows for a standardized connection between the hot water source 110 of the facility 102 and the existing steam main of the same or different facility 102.

[0131] In addition, in some embodiments, the heat pump system 104 is connected to a steam condensate return (e.g., the steam condensate return 214 of any one of FIGS. 2 to 5 , etc.). For example, in some embodiments, the heat pump system 104 is connected between steam condensate returns 214 configured to capture waste condensate from an existing steam main of the first facility 102-1, which allows the heat pump system 104 to generate high pressure steam 140 that is otherwise exhausted by the first facility 102-1 by recycling the steam condensate return 214. In some embodiments, the heat pump system 104 is connected between steam condensate returns 214 configured to capture waste condensate from a second facility 102-2 that is different from the first facility 102-1. However, the present disclosure is not limited thereto.

[0132] In some embodiments, connecting the heat pump system 104 between the hot water source 110 of the facility 102 and an existing steam main of the same or a different facility 102 further connects the heat pump system 104 to one or more utilities of the facility 102. For example, referring briefly to Fig. 9In some embodiments, the heat pump system 104 is further connected to a power source of the facility 102 (e.g., Fig. 9 986), which allows electrical communication between the facility 102 and the heat pump system 104 to deliver electricity (e.g., Figure 1B The power 150) is used by the heat pump system 104, for example, to drive one or more motors of a compressor group (eg, the compressor group 202 of any one of Figures 2 to 5, etc.) of the heat pump system 104.

[0133] It should be noted that in various embodiments of the present application, “connected” broadly means “directly connected” or “indirectly connected” via an additional structure.

[0134] refer to Figure 8At block 806 of the method 800, 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 the hot water from the hot water source 110 at a first temperature. In some embodiments, the first temperature of the hot water received by the heat pump system 104 is between 60 degrees Fahrenheit (℉) (15.6 degrees Celsius (℃)) and 150℉ (65.6℃). In some embodiments, the first temperature of the hot water received by the heat pump system 104 is between 60℉ (15.6℃) and 220℉ (104℃). For example, in some embodiments, the heat pump system 104 is configured to receive hot water from the hot water source 110 at a first temperature between 60°F (15.6°C) and 220°F (65.6°C), between 60°F (15.6°C) and 205°F (96.1°C), between 60°F (15.6°C) and 190°F (87.8°C), between 60°F (15.6°C) and 175°F (79.4°C), between 60°F (15.6°C) and 150°F (65.6°C), between 60°F (15.6°C) and 135°F (57.2°C), or between 60°F (15.6°C) and 190°F (87.8°C). ), between 60℉(15.6℃) and 120℉(48.9℃), between 60℉(15.6℃) and 105℉(40.6℃), between 60℉(15.6℃) and 90℉(32.2℃), between 60℉(15.6℃) and 75℉(23.9℃), between 80℉(26.7℃) and 220℉(65.6℃), between 80℉(26.7℃) and 205℉(96.1℃), between 80℉(26.7℃) and 190℉(87.8℃), between 80℉(26.7℃) and 175℉( 79.4℃), between 80℉(26.7℃) and 150℉(65.6℃), between 80℉(26.7℃) and 135℉(57.2℃), between 80℉(26.7℃) and 120℉(48.9℃), between 80℉(26.7℃) and 105℉(40.6℃), between 80℉(26.7℃) and 90℉(32.2℃), between 100℉(37.8℃) and 220℉(65.6℃), between 100℉(37.8℃) and 205℉(96.1℃), between 100℉(37. 8℃) and 190℉(87.8℃), between 100℉(37.8℃) and 175℉(79.4℃), between 100℉(37.8℃) and 150℉(65.6℃), between 100℉(37.8℃) and 135℉(57.2℃), between 100℉(37.8℃) and 120℉(48.9℃), between 100℉(37.8℃) and 105℉(40.6℃), between 120℉(48.9℃) and 220℉(65.6℃), between 120℉(48.9℃) and 205℉(96.2℃), between 100℉(37.8℃) and 120℉(48.9℃), between 100℉(37.8℃) and 105℉(40.6℃), between 120℉(48.9℃) and 220℉(65.6℃), between 120℉(48.9℃) and 205℉(96.2℃).1°C), between 120°F (48.9°C) and 190°F (87.8°C), between 120°F (48.9°C) and 175°F (79.4°C), between 120°F (48.9°C) and 150°F (65.6°C), between 120°F (48.9°C) and 135°F (57.2°C), between 140°F (60.0°C) and 220°F (65.6°C), between 140°F (60.0°C) and 205°F (96.1°C), between 140°F (60.0°C) and 190°F (87.8°C), between 140°F (60.0°C) and Between 175℉(79.4℃), between 140℉(60.0℃) and 150℉(65.6℃), between 175℉(79.4℃) and 220℉(65.6℃), between 175℉(79.4℃) and 205℉(96.1℃), between 175℉(79.4℃) and 190℉(87.8℃), between 190℉(87.8℃) and 220℉(65.6℃), between 190℉(87.8℃) and 205℉(96.1℃), or between 205℉(96.1℃) and 220℉(65.6℃), including the end values. In some embodiments, the first temperature received by the heat pump system 104 from the hot water source 110 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), at least 105°F (40.6°C), at least 110°F (43.3°C), at least 115°F (46.1°C), at least 120°F (48.9°C), at least 125°F (51.7°C), at least 130°F (54.4°C), at least 135°F ( .8°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 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), up to 85°F (29.4°C), up to 90°F (32.2°C), up to 95°F (35.0°C), up to 100°F (37.8°C), up to 105°F (40.6°C), up to 110°F (43.3°C), up to 115°F (46.1°C), up to 120°F (48.9°C), up to 125°F (51.7°C), up to 130°F (54.4°C), up to 135°F (57.2°C), up to 140°F (60.0°C), up to 145°F (62.8°C), up to 150°F (65.6°C). ), up to 155℉(68.3℃), up to 160℉(71.1℃), up to 165℉(73.9℃), up to 170℉(76.7℃), up to 175℉(79.4℃), up to 180℉(82.2℃), up to 185℉(85.0℃), up to 190℉(87.8℃), up to 195℉(90.6℃), up to 200℉(93.3℃), up to 205℉(96.1℃), up to 210℉(98.9℃), up to 215℉(102℃), or up to 220℉(104℃). For example, in some embodiments, hot water source 110 is used to receive low-grade heat in the form of hot water that is derived from an existing, commonly available on-site heat source, such as cooling water return from a cooling tower process, which is typically at a temperature between 85°F (29.4°C) and 90°F (32.2°C). In some embodiments, the low-grade heat in the form of hot water is derived from a dryer exhaust that is 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 an inlet of system 104 that allows heat from the hot water to be transferred to a heat pump water loop of system 104 via the heat exchange mechanism. For example, in some embodiments, the heat exchange mechanism is configured to produce condensed water (e.g., . Figure 1A Condensed water 180). However, the present disclosure is not limited thereto.

[0135] In some embodiments, the system 104 further comprises a water circuit, such as a closed water circuit configured as. In some embodiments, the water circuit comprises an upstream portion and a downstream portion. In some embodiments, the downstream portion is configured to receive hot water from the same facility or a different facility. In some embodiments, the upstream portion is configured to supply cooling water to the same facility or a different facility. In addition, in some embodiments, the water circuit is heated by the same facility or a different facility.

[0136] refer to Figure 8 At block 808, method 800 includes passing hot water through the heat pump system 104 to generate high pressure steam (e.g., Figure 8 Method 800 of high pressure steam, Figure 1BHigh pressure steam 140-1 or 140-2, Figures 1A to 7 High pressure steam 140 of any one of them, etc.).

[0137] For example, in some embodiments, the heat pump system 104 includes a compressor group (eg, the compressor group 202 of any one of FIGS. 2 to 5 , etc.) and a flash evaporator group (eg, Figures 2A to 5B , the method 800 utilizes the compressor group and the flasher group together to produce high pressure steam 140 for the facility 102.

[0138] More particularly, in some embodiments, passing the hot water through the heat pump system 104 to generate the high pressure steam 140 includes expanding the hot water at a flasher (e.g., the first flasher 212-1 of any one of FIGS. 2 to 5, etc.). By expanding the hot water at the flasher 212, the flasher 212 generates the low pressure steam 206 that is further utilized by the compressor unit 202. In addition, in some such embodiments, due to the expansion of the hot water within the flasher 212, the low pressure steam 206 generated by the flasher 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 by the first flasher 212-1 is less than the first temperature of the hot water source 110. In addition, in some such embodiments, when generating the low pressure steam 206, the flasher 212 operates in a passive steady state, which increases the efficiency of the heat pump system 104. However, the present disclosure is not limited thereto.

[0139] In some embodiments, method 800 is configured to operate at a pressure between 0.256 pounds per square inch (PSI) (17.7 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 ... r), between 0.35PSI(24.1mBar) and 3.2PSI(221mBar), between 0.35PSI(24.1mBar) and 2.7PSI(186mBar), between 0.35PSI(24.1mBar) and 1.2PSI(82.7mBar), between 0.35PSI(24.1mBar) and 0.7PSI(48.3mBar), between 0.85PSI(58.6mBar) and 3.72PSI(257mBar), between 0.85PSI(58.6mBar) and 3.2PSI(221mBar), between 0.85PSI(58.6mBar) and 2.7PSI(1 86mBar), 0.85PSI(58.6mBar) and 1.2PSI(82.7mBar), 1.35PSI(93.1mBar) and 3.72PSI(257mBar), 1.35PSI(93.1mBar) and 3.2PSI(221mBar), 1.35PSI(93.1mBar) and 2.7PSI(186mBar), 1.85PSI(128mBar) and 3.72PSI(257mBar), 1.85PSI(128mBar) and 3.2PSI(221mBar), 1.85PSI(128mBar) and 2.7PSI(186mBar), The first low-pressure steam 206-1 is produced at a first pressure between PSI (186mBar), between 2.35PSI (162mBar) and 3.72PSI (257mBar), between 2.35PSI (162mBar) and 3.2PSI (221mBar), between 2.35PSI (162mBar) and 2.7PSI (186mBar), between 2.85PSI (197mBar) and 3.72PSI (257mBar), between 2.85PSI (197mBar) and 3.2PSI (221mBar), or between 3.35PSI (231mBar) and 3.72PSI (257mBar), including end values.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 1.65 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 (89.6 mBar), at most 1.35 PSI (93.1 mBar), at most 1.5 PSI (103 mBar), at most 1.65 PSI (114mBar), up to 1.85PSI (128mBar), up to 2PSI (138mBar), up to 2.2PSI (152mBar), up to 2.35PSI (162mBar), up to 2.5PSI (172mBar), up to 2.7PSI (186mBar), up to 2.85PSI (197mBar), up to 3PSI (207mBar), up to 3.2PSI (221mBar), up to 3.35PSI (231mBar), up to 3.5PSI (241mBar) or up to 3.72PSI (257mBar).

[0140] In some embodiments, when the hot water is passed through the heat pump system 104, the expansion of the hot water at the flasher 212 further produces cooled water (e.g., condensed water) from the hot water. In some embodiments, the cooled water produced by the flasher 212 has a lower temperature than the hot water. In other words, in some such embodiments, the third temperature of the cooled water produced by the flasher 212 is less than the first temperature of the hot water source 110. In addition, in some embodiments, the third temperature of the cooled water is less than the second temperature of the low-pressure steam 206 produced by the flasher 212. Therefore, by expanding the hot water at the flasher 212, the heat pump system 104 increases the thermal energy of a portion of the hot water received from the hot water source 110 by forming the low-pressure steam 206, which is transferred from the cooled water produced by the flasher 212. For example, in some embodiments, the facility 102 is configured to utilize the high-pressure steam 140 produced by the system 104, which in turn produces the cooling water source 120 at a third temperature less than the first temperature of the hot water received from the hot water source 110. However, the present disclosure is not limited thereto.

[0141] Furthermore, in some embodiments, the pressure in the flash evaporator 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 to a first higher-pressure steam having a pressure higher than the low-pressure steam. For example, briefly referring to Figure 2A In some embodiments, the first low-pressure steam 206 at the first pressure is further compressed by a second compressor 204-2, which produces a first higher-pressure steam having a pressure higher than the first low-pressure steam, such as a second low-pressure steam 206-2 produced by the second compressor 204-2, which has a higher pressure than the first low-pressure steam 206-1 produced by the first compressor 204-1. Therefore, in some such embodiments, the first higher-pressure steam having a pressure higher than the first low-pressure steam includes the low-pressure steam 206 produced by one or more compressors 204 downstream of the first compressor 204-1 that produces the first low-pressure steam 206-1. However, the present disclosure is not limited thereto. For example, in some embodiments, the first higher-pressure steam having a pressure higher than the first low-pressure steam includes the high-pressure steam 140 produced by the heat pump system 104 for use by the facility 102.

[0142] In some embodiments, passing the hot water through the heat pump system 104 further includes introducing the hot water into the first higher pressure steam (e.g., the first low pressure steam 206-1 produced by the first flasher 212-1 of any one of FIGS. 2 to 5, the second low pressure steam 206-2 produced by the second flasher 212-2 of any one of FIGS. 2 to 5, ... the low pressure steam n 206-n produced by the flasher n 212-n, etc.). In some embodiments, the hot water is introduced into the first higher pressure steam so as to desuperheat the first higher pressure steam into a saturated first higher pressure steam.

[0143] In some embodiments, passing the hot water through the heat pump system 104 further includes repeating the compressing and introducing steps a desired number of times to generate high pressure steam.

[0144] In some embodiments, the desired number is greater than one. In some embodiments, the desired number is greater than one but less than twenty-one. In some embodiments, the desired number is between two and twenty, between two and seventeen, between two and fifteen, between two and twelve, between two and nine, between two and six, between two and three, between three and twenty, between three and seventeen, between three and fifteen, between three and twelve, between three and nine, between three and six, between five and twenty, between five and seventeen, between five and fifteen, between five and twelve, between five and nine, between five and six, between seven and twenty, between seven and seventeen, between seven and fifteen, between seven and twelve, between seven and nine, between nine and twenty, between nine and seventeen, between nine and fifteen, between nine and twelve, between eleven and twenty, between eleven and seventeen, between eleven and fifteen, between eleven and twelve, between thirteen and twenty, between thirteen and seventeen, between thirteen and fifteen, between fifteen and twenty, between fifteen and seventeen, or between seventeen and twenty, inclusive. In some embodiments, the desired number is at least two, at least three, at least four, at least five, at least six, at least seven, at least eight, at least nine, at least ten, at least eleven, at least twelve, at least thirteen, at least fourteen, at least fifteen, at least sixteen, at least seventeen, at least eighteen, at least nineteen, or at least twenty. In some embodiments, the desired number is at most two, at most three, at most four, at most five, at most six, at most seven, at most eight, at most nine, at most ten, at most eleven, at most twelve, at most thirteen, at most fourteen, at most fifteen, at most sixteen, at most seventeen, at most eighteen, at most nineteen, or at most twenty.

[0145] refer to Figure 8 At block 810 , in some embodiments, the method 800 includes supplying the high pressure steam 140 from the heat pump system 104 to an existing steam main of the same or a different facility 102 from which the heat pump system 104 receives hot water.

[0146] In some embodiments, the high pressure steam 140 is supplied at a rate of between 10 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 ...50 klb / hr, between 10 klb / hr and 100 klb / hr, between 10 klb / hr and 50 klb / hr, between 10 klb / hr and 150 klb / hr, between 10 klb / hr and 100 klb / hr, between 10 klb / hr and 150 klb / hr, between 10 klb / hr and 100 klb / hr, between 10 klb / hr and 150 klb / hr, between 10 klb / hr and 1 A mass flow rate between r and 200 klb / hr, between 75 klb / hr and 150 klb / hr, between 75 klb / hr and 100 klb / hr, between 150 klb / hr and 300 klb / hr, between 150 klb / hr and 250 klb / hr, between 150 klb / hr and 200 klb / hr, between 225 klb / hr and 300 klb / hr, or between 225 klb / hr and 250 klb / hr is supplied from the heat pump system 104 to the same or different facility 102, inclusive. In some embodiments, the mass flow rate of high pressure steam produced 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 high pressure steam produced 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.

[0147] In this disclosure, unless explicitly stated otherwise, descriptions of devices and systems will include implementations of one or more computers. Fig. 9For purposes of the description in , computer system 900 is represented as a single device that includes all of the functionality of computer system 900. However, the present disclosure is not limited in this regard. For example, the functionality of computer system 900 may be distributed across any number of networked computers and / or reside on each of a number of networked computers and / or by being hosted on one or more virtual machines and / or containers at a remote location accessible across a communications network (e.g., communications network 984). Those skilled in the art will appreciate that a variety 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. In addition, the devices and systems shown may transmit information wirelessly between each other, rather than relying on a physical communications network 984. Thus, Fig. 9 The exemplary topologies shown in are merely intended to describe features of some embodiments in a manner that will be readily understood by those skilled in the art.

[0148] Fig. 9 FIG. 9 is a block diagram showing an example 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 heat pump system (eg, FIG. 1 to FIG. 2 ). Figure 7 In some embodiments, the computer system 900 is associated with a facility (e.g., Figure 3 The first facility 102-1, Figures 1A to 7 A heat pump system 104 of any one of Figure 1A In some embodiments, the computer system 900 is associated with at most one facility or at most two or more facilities 102.

[0149] In some embodiments, the communication network 984 optionally includes the Internet, one or more local area networks (LANs), one or more wide area networks (WANs), other types of networks, or combinations of such networks. Examples of the communication network 984 include the World Wide Web (WWW), an intranet and / or a wireless network (e.g., a cellular telephone network), a wireless local area network (LAN) and / or a metropolitan area network (MAN), and other means of wireless communication. Wireless communication may optionally use any of a variety of communication standards, protocols, and technologies, including Global System for Mobile Communications (GSM), Enhanced Data GSM Environment (EDGE), High Speed ​​Downlink Packet Access (HSDPA), High Speed ​​Uplink Packet Access (HSUPA), Evolution-Data Only (EV-DO), HSPA, HSPA+, Dual Cell HSPA (DC-HSPDA), Long Term Evolution (LTE), Near Field Communication (NFC), Wideband Code Division Multiple Access (W-CDMA), Code Division Multiple Access (CDMA), Time Division Multiple Access (TDMA), Bluetooth, Wireless Fidelity (Wi-Fi) (e.g., IEEE 802.11a, IEEE 802.11ac, IEEE 802.11ax, IEEE 802.11b, IEEE 802.11g, and / or IEEE 802.11n), Voice over Internet Protocol (VoIP), Wi-MAX, email protocols (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 Information and Presence Extensions (SIMPLE), Instant Messaging and Presence Service (IMPS)) and / or Short Message Service (SMS), or any other suitable communication protocol, including communication protocols that have not been developed as of the filing date of this document.

[0150] In various embodiments, computer system 900 includes one or more processing units (CPUs) 972 , a network or other communications interface 974 , and memory 992 .

[0151] In some embodiments, the computer system 900 includes a user interface 976. The user interface 976 typically includes a display 978 for presenting a medium, such as a corresponding instrument (e.g., Fig. 9In some embodiments, the display 978 is integrated into the computer system (e.g., housed in the same chassis as the CPU 972 and the memory 992). In some embodiments, the computer system 900 includes one or more input devices 980 that allow an individual to interact with the computer system 900. In some embodiments, the input device 980 includes a keyboard, a mouse, and / or other input mechanism. Alternatively or in addition, in some embodiments, the display 978 includes a touch-sensitive surface (e.g., where the display 978 is a touch-sensitive display, or the computer system 900 includes a touchpad).

[0152] In some embodiments, the computer system 900 presents media to the user through a display 978. Examples of media presented by the display 978 include one or more images, videos, audio (e.g., waveforms of audio samples), or a combination thereof. In a typical embodiment, one or more images, videos, audio, or a combination thereof are presented by the display 978 through a client application stored in the memory 992. In some embodiments, audio is presented by an external device (e.g., a speaker, a headset, an input / output (I / O) subsystem, etc.), which receives audio information from the computer system 900 and presents audio data based on this audio information. In some embodiments, the user interface 976 also includes an audio output device, such as a speaker or an audio output for connecting to a speaker, a headset, or a headset.

[0153] The memory 992 includes high-speed random access memory, such as DRAM, SRAM, DDR RAM or other random access solid-state memory devices, and optionally also includes non-volatile memory, such as one or more magnetic disk storage devices, optical disk storage devices, flash memory devices or other non-volatile solid-state storage devices. The memory 992 may optionally include one or more storage devices remotely located from one or more CPUs 972. The memory 992 or one or more non-volatile memory devices in the memory 992 alternatively include non-temporary computer-readable storage media. The access to the memory 992 by other components of the computer system 900 (such as one or more CPUs 972) is optionally controlled by the controller. In some embodiments, the memory 992 may include a large-capacity storage device remotely located relative to one or more CPUs 972. In other words, some data stored in the memory 992 may actually be hosted on a device located outside the computer system 900 but can be accessed electronically by the computer system 900 using the communication interface 974 through the Internet, an intranet or other form of network 984 or an electronic cable.

[0154] In some embodiments, the memory 992 of the computer system 900 for generating high pressure steam stores:

[0155] ● Operating system 902 (e.g., ANDROID, iOS, DARWIN, RTXC, LINUX, UNIX, OS X, WINDOWS, or an embedded operating system such as VxWorks), which includes programs for handling various basic system services;

[0156] • Optionally, an electronic address 904 associated with the computer system 900 that identifies the computer system 900 (e.g., within the communication network 984, within a facility network, etc.);

[0157] A control module 906 that facilitates controlling one or more operations performed in generating high pressure steam according to a plurality of heuristic instructions, wherein the control module 906 includes a plurality of instruments 910 (e.g., Fig. 9 an instrument module 908 for recording a first instrument 910-1, a second instrument 910-2, ... an instrument 910-Q), and further comprising a task module 912 storing a plurality of tasks 914, each task 914 defining an operation for generating high pressure steam at a heat pump system according to one or more parameters 916 associated with the corresponding task 914; and

[0158] Optionally, a client application 918 for presenting information (eg, media) using the display 978 of the computer system 900, such as a method for generating high pressure steam (eg, Figure 8 The status of the steps and / or processes of method 800).

[0159] As noted above, an optional electronic address 904 is associated with the computer system 900. The optional electronic address 904 is used to uniquely identify the computer system 900 from at least other devices and components of the distributed system 900 (e.g., other devices (e.g., facilities 102) that access the communication network 984). For example, in some embodiments, the electronic address 904 is used to receive a request from a remote device associated with the first facility 102-1 to begin using the computer system 900 to generate high pressure steam for use by the second facility 102-2. However, the present disclosure is not limited in this regard. In some embodiments, the electronic address 904 is used to receive a request from a remote device associated with the first facility 102-1 to begin using the computer system 900 to generate high pressure steam for use by the first facility 102-1.

[0160] In some embodiments, the computer system 900 includes a control module 906, hereinafter referred to as a "controller", which is configured to control one or more operations performed when generating high pressure steam. Specifically, the controller 906 is configured to control one or more operations performed when generating high pressure steam according to a plurality of heuristic instructions. As a non-limiting example, in some embodiments, the plurality of heuristic instructions include one or more proportional, integral and derivative (PID) loop instructions and / or one or more variable frequency drive (VFD) instructions. For example, in some embodiments, the controller 906 communicates with one or more sensors (e.g., Fig. 9 The controller 906 is in electronic communication with one or more sensors 982, wherein each sensor 982 of the one or more sensors 982 is configured to determine a state associated with a corresponding instrument 910. In some embodiments, the controller 906 is in electronic communication with one or more sensors 982, wherein the one or more sensors include: a first sensor set 982 configured to determine a state associated with a system (e.g., Figure 8 The method 800 of the heat pump system of FIG. 1 to Figure 7a second sensor set 982 configured to determine one or more pressures associated with the system 104 (e.g., an internal pressure of the flasher group, a pressure ratio of the compressor group, a pressure loss at some or all of the system 104, etc.); a third sensor set 982 configured to determine one or more flow rates associated with the system 104 (e.g., a flow rate of hot water received by the system 104 ... 982, which is configured to determine one or more speeds associated with the system 104 (e.g., the speed of hot water received by the system 104, the speed of low-pressure steam generated by the flasher group 210 of the system 104, the speed of high-pressure steam generated by the compressor group 202 of the system, the speed of steam condensate water source received by the system 104, etc.); a fifth sensor set 982, which is 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 arc flashes, one or more groundings, etc.); or a combination thereof. Thus, by electronically communicating with one or more sensors 982, the controller 906 allows the computer system 900 to control the flow rate of high-pressure steam generated by the system 104 and received by the facility 102. However, the present disclosure is not limited thereto.

[0161] The apparatus 910 is a device that performs a specific function or functions in the system 104 to generate high pressure steam, such as generating a high pressure steam product associated with the system 104 (e.g., Figure 8 Method 800 of high pressure steam, Figure 1A High pressure steam 140-1 or 140-2, Figures 2A to 7 any of the high pressure steam 140, etc.) or cooling water products (e.g., Figures 1A to 6 For example, in some embodiments, each respective instrument 910 in the plurality of instruments 910 is configured to perform a specific task 914 or multiple tasks 914 in the system 104 to generate high pressure steam 140. Examples of instruments 910 include, but are not limited to, blowers, boilers (e.g., heat recovery boilers, Figure 5A2 ), a first conduit for conveying hot water received by the hot water source 110 of FIG. 2 , a second conduit for conveying the low-pressure steam 206 generated by the flash evaporator 212, etc.), a desuperheater (e.g., Figure 5A The first desuperheater 232-1 in the desuperheater group 230, etc.), a drum, a heat exchanger, a pump (e.g., Figure 5A reboost pump 220, etc.), pipes, reservoirs, valves (e.g., Figure 3 valve 218-1, etc.), a container (e.g., a flash evaporator), etc. For example, in some embodiments, one or more instruments 910 include a compressor group 202, which further includes a series of at least two compressors 204, which are configured to supply high pressure steam 140 to a facility (e.g., Figure 1A The existing steam main of the facility 102-1) (e.g., Figure 8 However, the present disclosure is not limited thereto.

[0162] In some embodiments, each task 914 is associated with a function, step, or process (e.g., Figure 8 As a non-limiting example, in some embodiments, one or more tasks 914 for generating high pressure steam 940 include receiving hot water (e.g., Figure 8 806), 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., Figure 8 808), expanding the hot water at a flash evaporator (e.g., Figure 8 808), generating low pressure steam (e.g., Figure 8 808), produce cooled water (e.g., Figure 8 808), maintaining the flash vessel at a first pressure less than the saturation pressure of the hot water (e.g., Figure 8 808), compressing low pressure steam (e.g., Figure 8 808 of the present invention), desuperheating the low pressure steam, supplying the high pressure steam from the system 104 to the existing steam main of the facility 102 (e.g., Figure 8 Box 810), etc.

[0163] In addition, each task 914 includes a set of parameters 916 for performing functions by the corresponding instrument 910. In some embodiments, each task 914 is a definition of operations that are logical dependencies of functions performed by the corresponding instrument 910. For example, in some embodiments, the task 914 is a first operation of running a first instrument 910-1 with a first set of parameters 916, and the second task 914-2 is a second operation of running a second instrument 910-2. As a non-limiting example, in some embodiments, the parameters 916 include a temperature of hot water received by the system 104 from the hot water source 110, a pressure of the hot water received by the system 104 from the hot water source 110, a mass flow rate of the hot water received by the system 104 from the hot water source 110, a temperature of the low-pressure steam 206 generated by the system 104, a pressure of the low-pressure steam 206 generated by the system 104, a mass flow rate of the low-pressure steam 206 generated by the system 104, a temperature of the high-pressure steam 140 generated by the system 104, a pressure of the high-pressure steam 140 generated by the system 104, 140, the mass flow rate of the high pressure steam 140 generated by the system 104, the temperature of the cooling water received from the cooling water source 120 generated by the system 104, the pressure of the cooling water received from the cooling water source 120 generated by the system 104, the mass flow rate of the cooling water received from the cooling water source 120 generated by the system 104, the temperature of the steam condensate return 214 received by the system 104, the pressure of the steam condensate return 214 received by the system 104, the mass flow rate of the steam condensate return 214 received by the system 104, etc. As a non-limiting example, in some embodiments, the computer system 900 configures one or more parameters 916, including configuring a flow rate parameter 916 (e.g., mass flow rate), a pressure parameter 916, a temperature parameter 916, a direction parameter 916, etc. associated with the corresponding instrument 910, so as to optimize the generation of the high pressure steam 140 at the system 104. However, the present disclosure is not limited thereto.

[0164] Each of the modules and applications identified above corresponds to a program for performing one or more of the functions described above and the methods described in this disclosure (e.g., the computer-implemented methods and other information processing methods described herein, Figure 8 800, etc.). These modules (e.g., instruction sets) need not be implemented as individual software programs, procedures, or modules, and thus various subsets of these modules are optionally combined or otherwise rearranged in various embodiments of the present disclosure. In some embodiments, memory 992 optionally stores a subset of the modules and data structures identified above. In addition, in some embodiments, memory 992 stores additional modules and data structures not described above.

[0165] It should be understood that Fig. 9The computer system 900 is only one example of a computer system 900 , and the computer system 900 optionally has more or fewer components than shown, optionally combines two or more components, or optionally has a different configuration or arrangement of components. Fig. 9 The various components shown are implemented in hardware, software, firmware, or a combination thereof, including one or more signal processing and / or application specific integrated circuits.

[0166] Additional example embodiments of the heat pump system 400 are described below:

[0167] Example 1: A heat pump system of the present disclosure configured to connect modularly to an existing steam main of a facility.

[0168] In some embodiments, a heat pump system (e.g., Figures 1A to 7 any of the heat pump systems 104, etc.) configured to have products and / or facilities (e.g., Figure 1A Facility 102-1, Figure 1A More particularly, in some embodiments, the baseline heat pump system 104 is configured to receive hot water at a lowest specified temperature in the series of facilities 102, to produce high pressure steam 140 at a highest specified pressure in the series of facilities 102, and to provide high pressure steam at a maximum flow rate in the series of facilities 102. In some embodiments, for a facility 102 in the series of facilities 102 having an increased hot water temperature compared to other facilities in the series of facilities, the baseline heat pump system 104 is modified by reducing (e.g., removing) one or more compressors 204 at a downstream (e.g., low pressure) portion of the compressor train 202 of the facility 102. In some embodiments, for a facility 102 in the series of facilities 102 having a reduced outlet steam pressure, the baseline heat pump system 104 is modified by reducing (e.g., removing) one or more compressors 204 at an upstream (e.g., high pressure side) of the compressor train 202. In some embodiments, for a facility 102 in a series of facilities 102 having a reduced flow rate of high-pressure steam 140 , the baseline heat pump system 104 is modified by determining a first temperature of hot water received from the facility 102 and an outlet pressure of the high-pressure steam received by the facility 102 and then selecting an appropriate equipment size to support the desired flow rate of the high-pressure steam 140 .

[0169] In some embodiments, one or more components of system 104 are housed on modular skids or containers designed for ease of transportation and final installation.

[0170] In some embodiments, the baseline heat pump system 104 is configured to address the edge of the operating parameters 916, such as the minimum hot water source 110 temperature, the minimum steam condensate return 214 temperature, the maximum high pressure steam 140 temperature, the maximum high pressure steam 140 pressure, the 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 the flasher train 210 are reduced from the baseline 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 baseline heat pump system 104 is configured to address the minimum hot water source 110 temperature of at least 60 degrees Fahrenheit (℉) (15.6 degrees Celsius (℃)) or at least 80 ℉ (26.7℃) received from the facility 102.

[0171] In some embodiments, the baseline heat pump system 104 is modified by increasing the pressure of the flasher train 210 and decreasing one or more compressors 204 at the front end portion of the compressor train 202 based on a determination that the hot water source 110 is above 80°F (26.7°C).

[0172] In some embodiments, the baseline heat pump system 104 is modified by reducing one or more compressors 204 at the back end portion of the compressor train 202 based on a determination that the high pressure steam 140 received by the facility is less than 290 PSIg (20 Bar).

[0173] In some embodiments, based on a determination that the high pressure steam 140 requires a flow rate of less than 50 kilopounds (klb) / hour, one or more flashers 212 in the flasher group 210 and / or one or more compressors 204 in the compressor group 202 are replaced with corresponding one or more flashers 212 and / or one or more compressors 204 configured for the lower flow rate.

[0174] Since steam density increases with increasing pressure, the mass flow of a given size compressor 204 also increases. Therefore, in some embodiments, the systems, methods, and apparatus of the present disclosure utilize an upper boundary of an operating parameter, such as a 20 Barg output pressure of the high pressure steam 140, and determine the minimum flow rate at which the compressor group 202 produces such pressure with high efficiency and maximum compression ratio (e.g., after desuperheating via the desuperheater group 230). In some embodiments, at the minimum flow rate, the systems, methods, and apparatus of the present disclosure determine the inlet pressure of the hot water received from the hot water source 110 that is required to achieve a 20 Barg output pressure of the high pressure flow produced thereto. In some embodiments, the systems, methods, and apparatus of the present disclosure iteratively repeat this process on the remaining compressors 204 in the compressor group 202 until a 35 mBara inlet pressure of the hot water received by the system 104 is reached.

[0175] In some embodiments, the baseline heat pump system 104 is modified according to a unique set of parameter requirements associated with the performance of the heat pump system 104 and / or one or more processes performed at the facility. For example, in some embodiments, the unique set of parameter 916 requirements includes 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 systems, methods, and apparatuses of the present disclosure configure the baseline heat pump system 104 into two or more subassemblies. Each subassembly includes one or more compressors 204 in the compressor group 202, which are configured to be removed from the front end portion and / or the rear end portion of the compressor group 202. In some embodiments, each subassembly includes one or more flashers 212 in the flasher group 210. By modifying the baseline heat pump system 104 via the subassembly, the compressor group 202 is modified to change 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. Furthermore, in some embodiments, an alternative subassembly includes a smaller, lower flow compressor 204 that is substituted into the baseline heat pump system 104 to change the mass flow rate of high pressure steam 140 produced by the system 104 while optimizing the COP, cost, and size of the system 104 .

[0176] Thus, by providing the heat pump system 104 in a modular configuration, the present disclosure allows for a pre-engineered (eg, pre-configured) and / or factory-produced packaged system 104 ready to be connected to a pre-existing facility 102 .

[0177] Furthermore, in some embodiments, such modular configuration 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 providing the standardization needed to achieve economies of scale in manufacturing the heat pump system 104. Furthermore, in some embodiments, the modular configuration of the heat pump system 104 allows for production-level quality and reliability assurance by qualifying two or more sub-assemblies in addition to qualifying the incoming components of the heat pump system 104.

[0178] Additionally, in some embodiments, the modular configuration of the heat pump system 104 allows for factory fabrication of the heat pump system 104 in one or more skids, allows for transportation of the heat pump system 104 from the factory to the facility 102 via standard truck-based transportation, allows for simple, uncomplicated on-site installation of the one or more skids at defined interface points at the facility 102, allows for a minimized footprint, allows for easy removal and / or replacement of subassemblies, or a combination thereof.

[0179] For example, in some embodiments, the footprint (eg, the surface area below the system 104) is 2,000 square feet (ft2 ) and 8,000ft 2 Between, inclusive, such as a 150 foot long by 50 foot wide footprint of system 104.

[0180] Example 2: Computer system, method, and non-transitory computer-readable storage medium for configuring a heat pump system.

[0181] In some embodiments, the present disclosure provides computer systems, methods, and non-transitory computer-readable storage media for configuring the heat pump system 104 .

[0182] In some embodiments, the computer systems, methods, and non-transitory computer-readable storage media of the present disclosure allow for selection and configuration of one or more subassemblies of the heat pump system 104 to best meet a given set of parameter 916 requirements associated with the facility 102 .

[0183] In some embodiments, the computer systems, methods, and non-transitory computer-readable storage media of the present disclosure provide a lookup table. In some embodiments, the lookup table is utilized to match one or more ranges of various parameter requirements (e.g., a first temperature of hot water received from facility 102 and / or an outlet pressure of high-pressure steam received by facility 102 from system 104) with a specific combination of two or more subassemblies configured to operate together.

[0184] In some embodiments, the computer system, method, and non-transitory computer-readable storage medium of the present disclosure evaluate the performance of the heat pump system 104 based on a given set of 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 determine the given set of parameter 916 requirements in the lookup table, and then use the lookup table to select two or more subassemblies. In some embodiments, the computer system, method, and non-transitory computer-readable storage medium of the present disclosure evaluate the performance of the heat pump system 104 including two or more subassemblies selected by the lookup table. In some embodiments, the computer system, method, and non-transitory computer-readable storage medium of the present disclosure display a report that includes a complete, pre-qualified configuration of the heat pump system and two or more subassemblies ready for manufacture, as well as performance specifications of the configuration.

[0185] Example 3: Heat pump system.

[0186] refer to Figure 5A In some embodiments, the present disclosure provides a system 104 for generating high pressure steam.

[0187] In some embodiments, the system 104 includes a compressor train 202. The compressor train 202 includes a series of at least two compressors 204. In some embodiments, the series of at least two compressors 204 includes at least four compressors 204. In addition, the compressor train 202 includes an inlet 216 of the compressor train 202. In addition, the compressor train 202 includes an outlet 208 of the compressor train 202, which is configured to provide the high-pressure steam 140 to the facility 102. In some embodiments, the series of at least two compressors 204 is positioned to be inserted between the inlet of the compressor train 202 and the outlet of the compressor train 202.

[0188] In some embodiments, the system further includes a flasher group 210. The flasher group 210 includes a series of at least two flashers 212, wherein the series of at least two flashers further includes a terminal flasher 212 at one end of the flasher group 210. In some embodiments, the series of at least two flashers 212 includes at least four flashers 212. In addition, the vapor outlet 226 of the terminal flasher 212 is fluidly coupled to the inlet 216 of the compressor group 202. In addition, the system 104 includes a vapor outlet 226 of the rest of the series of at least two flashers 212, which is fluidly coupled between the compressors 204 in the series of at least two compressors 204.

[0189] In some embodiments, the system 104 is configured to receive hot water received from the hot water source 110 at a temperature of 120°F (48.9°C). In some embodiments, the system 104 is configured to receive the steam condensate return 214 at a temperature of 200°F (93.3°C).

[0190] In some embodiments, each flasher 212 in a series of at least two flashers 212 in the flasher bank 210 is configured to be maintained at an internal pressure less than the saturation pressure of hot water input into the corresponding flasher 212, and is configured to expand the hot water to produce low-pressure steam. For example, in some embodiments, the terminal flasher 212-1 is configured to be maintained at an internal pressure less than the saturation pressure of hot water at 120°F (48.9°C) (e.g., the saturation pressure of water at 120°F is 116.9 mBar, which produces an internal pressure of less than 116.8 mbar(a) for the corresponding flasher), the second flasher 212-2 is configured to be maintained at an internal pressure less than the saturation pressure of hot water at 140°F (60°C), the third flasher 212-3 is configured to be maintained at an internal pressure less than the saturation pressure of hot water at 160°F (71.1°C), and the fourth flasher 212-4 is configured to be maintained at an internal pressure less than the saturation pressure of hot water at 180°F (82.2°C). Thus, in some embodiments, the first terminal flasher (e.g., Figures 2A to 5BThe internal pressure of any of the flash evaporators 212-1, etc.) is configured to be maintained at a pressure less than the saturation pressure of the hot water received by the system 104 from the hot water source 110. In addition, in some embodiments, the second end flash evaporator (e.g., Figures 2A to 5B The internal pressure of the flash evaporator 212 - 2 , etc. of any one of the flash evaporators 212 - 2 , etc. is configured to be maintained at a pressure less than the saturation pressure of the steam condensate return 214 received by the system 104 .

[0191] All references cited herein are incorporated by reference in their entirety and for all purposes to the same extent as if each individual publication or patent or patent application was specifically and individually indicated to be incorporated by reference in its entirety for all purposes.

[0192] The present invention may be implemented as a computer program product comprising a computer program mechanism embedded in a non-transitory computer-readable storage medium. For example, the computer program product may contain program modules shown in any combination of the figures. These program modules may be stored on a CD-ROM, a DVD, a magnetic disk storage product, a USB key, or any other non-transitory computer-readable data or program storage product.

[0193] As will be apparent to those skilled in the art, many modifications and variations may be made to the present invention without departing from the spirit and scope of the present invention. The specific embodiments described herein are provided by way of example only. The embodiments are selected and described in order to best explain the principles of the present invention and its practical application, so as to enable others skilled in the art to best utilize the present invention and various embodiments with various modifications suitable for the intended specific use. The present invention is limited only by the terms of the appended claims and the full scope of equivalents authorized by these technical solutions.

Claims

1. A system for generating high pressure steam, the system comprising: A compressor unit comprising: A series of at least two compressors; the inlet of the compressor unit; and an outlet of the compressor train configured to provide high pressure steam to a facility; and A flash evaporator train comprising: a series of at least two flashers including a terminal flasher at one end of the flasher train, wherein a vapor outlet of the terminal flasher is fluidly coupled to the inlet of the compressor train; and The vapor outlet of the remainder of the series of at least two flashers is fluidly coupled between compressors in the series of at least two compressors.

2. The system of claim 1, wherein the flasher bank further comprises an inlet of the flasher bank, the inlet configured to receive hot water received from the facility or a different facility.

3. The system of claim 1 or 2, wherein the remaining portions of the series of at least two flash evaporators each include a liquid outlet fluidly coupled to an inlet of another of the series of at least two flash evaporators.

4. The system of any one of claims 1 to 3, wherein the terminal flasher comprises a liquid outlet fluidly coupled to an outlet of the system.

5. The system of claim 4, comprising a controller configured to maintain a temperature range of the flasher train within a range of a first temperature of the high pressure steam and a second temperature of the outlet of the system.

6. The system of any one of claims 1 to 5, wherein the series of at least two compressors comprises a centrifugal compressor, and wherein the system further comprises a controller configured to maintain the centrifugal compressor from choking or surging.

7. The system of claim 6, wherein the controller is configured to modify the rotational speed of a respective compressor in the compressor train, thereby maintaining a pressure at the outlet of the compressor train.

8. The system of any one of claims 1 to 7, wherein the terminal flasher comprises a liquid outlet fluidly coupled to a re-boosting pump coupled to an outlet of the system.

9. The system of any one of claims 1 to 8, wherein each flash evaporator in the series of at least two flash evaporators is configured to be maintained at an internal pressure less than a saturation pressure of hot water input into the corresponding flash evaporator, and to expand the hot water to produce low-pressure steam.

10. The system of any one of claims 1 to 9, wherein the terminal flasher further comprises an inlet configured to receive hot water received from the facility or a different facility.

11. The system of any one of claims 1 to 9, wherein the terminal flasher further comprises: an inlet configured to receive hot water received from the facility or a different facility, and A liquid outlet is fluidly coupled to a reboost pump coupled to an outlet of the system, wherein the outlet of the system is fluidly coupled to a heat exchange mechanism associated with the hot water received from the facility or the different facility.

12. The system of any one of claims 1 to 11, wherein a flasher in the flasher train comprises a continuous blowdown configured to remove contaminants contained by the flasher.

13. The system of any one of claims 1 to 12, wherein a flasher in the flasher bank comprises a second liquid outlet fluidly configured to selectively remove fluid from a corresponding flasher.

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

15. The system according to any one of claims 1 to 14, further comprising a desuperheater group, the desuperheater group comprising at least one desuperheater, wherein each desuperheater in the desuperheater group comprises an outlet configured to inject hot water received from the facility or a different facility into the compressor group.

16. The system of claim 15, wherein at least one desuperheater in the bank of desuperheaters is configured to control a flow rate of a fluid passing through the desuperheater.

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

18. The system of any one of claims 1 to 17, wherein the system comprises a coefficient of performance greater than 65% of the corresponding Carnot efficiency.

19. The system of any one of claims 1 to 18, further comprising a boiler disposed to be inserted between an output of a terminal compressor in the compressor train and the outlet of the compressor train and fluidly coupled to the output of the terminal compressor and the outlet of the compressor train.

20. The system of any one of claims 1 to 19, further comprising a steam accumulator disposed to be inserted between the output of a terminal compressor in the compressor train and the outlet of the compressor train and to fluidly couple the output of the terminal compressor and the outlet of the compressor train.

21. The system of any one of claims 1 to 20, wherein the compressor train comprises between two and twenty compressors, inclusive.

22. The system according to any one of claims 1 to 21, wherein The compressor unit comprises m compressors; and m is an integer greater than two and is selected based on the temperature of the high pressure steam and the temperature of hot water received from the facility or a different facility.

23. The system of any one of claims 1 to 22, wherein the series of at least two compressors includes at least four compressors, and wherein the at least four compressors are arranged in a herringbone array configuration.

24. The system of any one of claims 1 to 23, wherein each compressor in the compressor train and each flasher in the flasher train share a one-to-one relationship.

25. The system of any one of claims 1 to 24, wherein the compressor train comprises a first compressor and a second compressor, the first compressor comprising a first size, the second compressor comprising a second size smaller than the first size, and wherein the first compressor is coupled upstream of the second compressor in the compressor train.

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

27. The system of any one of claims 1 to 26, wherein each compressor in the compressor train comprises a compression ratio of less than 2.

5.

28. The system of any one of claims 1 to 27, wherein the outlet of the compressor unit is configured to provide 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. The system according to any one of claims 1 to 28, further comprising a water circuit, the water circuit comprising a downstream portion and an upstream portion, the downstream portion being configured to receive the hot water from the same facility or a different facility, the upstream portion being configured to supply cooling water to the same facility or the different facility, wherein the water circuit is heated by the same facility or the different facility.

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