Compressed gas storage and transport

Abstract

The split cooling system splits the first gas stream into a second stream and a third stream, expands and cools the third stream, and thereafter passes the second stream and the third stream through a heat exchanger to transfer heat from the second stream to the third stream. Thus, the pressure in the third stream is converted into cooling of the second stream. A vehicle transports cryogenic compressed hydrogen in a glass-reinforced storage tank whose strength increases as the temperature of the hydrogen decreases. The low-temperature compressed hydrogen can be transported in the insulating space cooled by the liquid nitrogen cooling system. Liquid nitrogen can be used as ballast in the storage tank. Various systems and methods securely store and transport compressed combustible or hazardous fluids, e.g., by controlling ventilation air exchange rates, delivering gases via a double-wall delivery hose, or sensing flames using a duct-based temperature sensor.

Description

[0001] Cross-reference to related applications

[0002] This application claims the benefit of priority to U.S. Provisional Patent Application No. 63 / 468,881, filed May 25, 2023, entitled “Compressed Gas Storage and Transportation,” the entire contents of which are incorporated herein by reference. background Technical Field

[0003] The various embodiments generally relate to vehicles used for transporting gases such as compressed natural gas or hydrogen. Background Technology

[0004] Gaseous fuels, such as natural gas, are typically transported via pipelines, although some natural gas users periodically require a supply exceeding what is available through existing pipelines. Additionally, there are areas where natural gas services are simply not possible via pipeline due to remoteness, the high cost of laying pipelines, or other factors. For such areas, natural gas can be transported via CNG tanks, as described, for example, in PCT Publications WO2014 / 031999 and 2018 / 144328, the entire contents of each of which are incorporated herein by reference.

[0005] Natural gas and hydrogen are typically transported via waterways (e.g., rivers, lakes, bays, seas, oceans) in the form of liquefied natural gas (LNG) and liquid hydrogen (LH). However, LNG and LH require complex and expensive liquefaction plants and special handling on both the supply and transportation sides. LNG and LH also need to be regasified during transportation, which involves the use of large amounts of heat and complex cryogenic heat exchangers, as well as cryogenic transportation / storage equipment. Summary of the Invention

[0006] One or more non-limiting embodiments provide a method for cooling a compressed gas. The method includes: splitting a first stream of compressed gas into a second stream and a third stream; expanding and cooling the third stream; and passing the third stream and the second stream downstream of the expanded and cooled third stream through a heat exchanger that transfers heat from the second stream to the third stream.

[0007] According to one or more embodiments of these embodiments, the heat exchanger includes a first heat exchanger, and the method further includes: passing the third stream and the first stream through a second heat exchanger downstream of the third stream leaving the first heat exchanger, the second heat exchanger transferring heat from the first stream to the third stream.

[0008] According to one or more embodiments of these embodiments, the method includes: actively cooling the first stream after the first stream leaves the second heat exchanger.

[0009] According to one or more embodiments of these examples, the expansion cooling includes JT cooling.

[0010] According to one or more embodiments of these embodiments, the expansion cooling includes passing a third flow through a turbine expander.

[0011] According to one or more embodiments of these embodiments, the method includes controlling the flow rate of the second stream relative to the third stream to ensure that the temperature of the second stream is within a predetermined temperature range when it leaves the heat exchanger.

[0012] According to one or more embodiments of these embodiments, the method includes: compressing a third stream downstream of a heat exchanger to form a fourth stream; and merging the fourth stream and a fifth stream to form a first stream.

[0013] One or more embodiments provide a system for cooling compressed gas. The system includes: a compressed gas inlet for receiving compressed gas; a heat exchanger; a distributor; an expansion cooler; a compressed gas outlet; a first channel extending from the inlet to the distributor; a second channel extending sequentially from the distributor through the heat exchanger and to the compressed gas outlet; and a third channel extending sequentially from the distributor through the expansion cooler and through the heat exchanger.

[0014] According to one or more embodiments of these embodiments, the system includes a cooling unit disposed in a first channel.

[0015] According to one or more embodiments of these embodiments: the heat exchanger includes a first heat exchanger; the system further includes a second heat exchanger; the first channel passes through the second heat exchanger; and the third channel sequentially passes from the splitter through the expansion cooler, through the first heat exchanger, and then through the second heat exchanger.

[0016] One or more embodiments provide an assembly for transporting cryogenic compressed hydrogen. The assembly includes: a vehicle; an insulated space supported by the vehicle; a glass-reinforced storage tank disposed within the insulated space, the storage tank defining an internal space; and cryogenic compressed hydrogen stored within the tank. According to one or more embodiments of these embodiments, the pressure inside the tank is between 900 psig and 10000 psig, and the temperature inside the tank is between 60 K and 210 K.

[0017] According to one or more embodiments of these examples, the density of cryogenic compressed hydrogen in the tank is at least 1.0 lbm / ft. 3 .

[0018] According to one or more embodiments of these examples, cryogenic compressed hydrogen occupies at least 75% of the tank volume.

[0019] According to one or more embodiments of these examples, the vehicle includes a vessel.

[0020] According to one or more embodiments of these embodiments, the assembly includes a pressure relief valve operably connected to the tank, and the pressure relief valve is configured to discharge gas from the tank to the surrounding environment outside the vehicle when the pressure exceeds a predetermined pressure.

[0021] According to one or more embodiments of these examples, the pressure relief valve includes an emergency rupture disc.

[0022] According to one or more embodiments of these embodiments, the assembly includes a pressure relief valve operably connected to an insulating space, and the pressure relief valve is configured to discharge gas from the insulating space to the surrounding environment outside the vehicle if the pressure within the insulating space exceeds a predetermined pressure.

[0023] According to one or more embodiments of these examples, the predetermined pressure relative to the ambient pressure is between 0.1 psi and 3.0 psi.

[0024] According to one or more embodiments of these examples, the pressure relief valve includes an emergency burst hatch.

[0025] According to one or more embodiments of these examples, the tank comprises a composite reinforcing material.

[0026] According to one or more embodiments of these examples, the can contains glass that is stronger at the temperature than at 273K.

[0027] According to one or more embodiments of these examples, the tank includes a lined storage cylinder, wherein the lining comprises HDPE, PA-6, UHMWPE, or 316L stainless steel.

[0028] According to one or more embodiments of these examples, the assembly includes an overflow valve operably connected to the tank.

[0029] According to one or more embodiments of these embodiments, the vehicle may be a ship, a wheeled vehicle (e.g., a truck and trailer, a railcar), or a barge.

[0030] One or more embodiments provide an assembly for transporting cryogenic compressed hydrogen. The assembly includes: a vehicle; an insulated space supported by the vehicle; liquid nitrogen disposed within the insulated space; a storage tank disposed within the insulated space defining an internal space; and cryogenic compressed hydrogen stored within the tank. According to one or more embodiments of these embodiments, the pressure within the tank is between 900 psig and 10000 psig, and the temperature within the tank is between 60 K and 210 K.

[0031] According to one or more embodiments of these examples, the liquid nitrogen disposed in the insulating space is disposed on the outside of the tank.

[0032] According to one or more embodiments of these embodiments, the assembly includes: a nitrogen liquefaction system supported by the vehicle and configured to liquefy gaseous nitrogen; a liquid nitrogen channel operatively connecting the liquefaction system to the insulating space and configured to transfer liquid nitrogen from the liquefaction system to the insulating space; and a nitrogen return channel operatively connecting the insulating space to the liquefaction system and configured to transfer gaseous nitrogen from the insulating space to the liquefaction system, such that the liquefaction system can liquefy gaseous nitrogen received from the insulating space via the nitrogen return channel.

[0033] According to one or more embodiments of these examples, the liquefaction system is configured to maintain the pressure within the insulated space at 0.1 psig to 2.0 psig relative to the ambient pressure outside the vehicle.

[0034] According to one or more embodiments of these examples, the insulating space includes a recess that is shaped and configured to collect and retain liquid nitrogen.

[0035] According to one or more embodiments of these examples, the assembly includes a nitrogen generator configured to collect nitrogen and isolate nitrogen from ambient air, and to provide isolated nitrogen to an insulated space, wherein the isolated nitrogen is at least 90%, 91%, 92%, 93%, 94%, 95%, 96%, 97%, 98%, 99%, 99.9%, and / or 99.99% nitrogen.

[0036] According to one or more embodiments of these examples, the nitrogen generator includes a compressor and a pressure swing absorption device, the compressor being configured to compress ambient air and the pressure swing absorption device being configured to separate nitrogen from the compressed air.

[0037] According to one or more embodiments of these examples, the storage tank includes a glass-reinforced storage tank.

[0038] According to one or more embodiments of these embodiments, liquid nitrogen disposed in an insulating space is disposed in an internal space.

[0039] According to one or more embodiments of these embodiments, the tank includes a gas port and a liquid port, the gas port being fluidly connected to an upper portion of the interior space and the liquid port being fluidly connected to a lower portion of the interior space.

[0040] According to one or more embodiments of these examples, the assembly includes a baffle disposed within the tank.

[0041] According to one or more embodiments of these embodiments, the assembly includes a float in an internal space that is capable of vertical movement within the internal space, the float dividing the internal space into an upper portion above the float and a lower portion below the float, the float having a density higher than that of the cryogenic compressed hydrogen and lower than that of the liquid nitrogen.

[0042] According to one or more embodiments of these embodiments, the assembly includes: a liquid nitrogen storage container; a liquid nitrogen supply channel connecting the container to a tank; and a pump positioned and configured to pump liquid nitrogen from the container into an internal space.

[0043] According to one or more embodiments of these embodiments, the pump is configured to pump liquid nitrogen into the interior space during the unloading of cryogenic compressed hydrogen from the tank in order to displace the cryogenic compressed hydrogen in the interior space and to facilitate the substantially isothermal and isobaric unloading of the cryogenic compressed hydrogen from the tank.

[0044] According to one or more embodiments of these embodiments, the assembly includes:

[0045] A liquid nitrogen return channel that connects the liquid nitrogen storage container to the internal space; and a valve disposed in the liquid nitrogen return channel, the valve having an open state in which liquid nitrogen can flow from the internal space to the container, and a closed state to prevent liquid nitrogen from flowing from the internal space to the container.

[0046] According to one or more embodiments of these embodiments, the valve includes a pressure regulating valve configured to open when the pressure in the tank exceeds a predetermined pressure.

[0047] According to one or more embodiments of these examples, the valve is configured to facilitate substantially isobaric loading of the tank with cryogenic compressed hydrogen.

[0048] One or more embodiments provide a method for transporting cryogenic compressed hydrogen using a vehicle having an insulated space and a storage tank disposed within the insulated space, the storage tank defining an interior space. The method includes: cooling the temperature within the interior space to between 77K and 90K; pressurizing the interior space to a pressure between 900 psig and 10000 psig (and / or between 2000 psig and 7500 psig); and delivering cryogenic compressed hydrogen into the interior space while the temperature is between 60K and 210K (and / or between 77K and 90K) and the pressure is between 900 psig and 10000 psig (and / or between 2000 psig and 7500 psig).

[0049] According to one or more embodiments of these examples, the cooling occurs when the pressure within the internal space is less than 300 psig.

[0050] According to one or more embodiments of these examples, the cooling includes placing liquid nitrogen in an insulated space outside the tank when the pressure inside the internal space is less than 300 psig.

[0051] One or more embodiments provide a method of manufacturing a storage tank for storing a compressed fluid. The method includes: inserting an expandable support through a hole into a liner; radially expanding the support within an internal space inside the liner to mechanically support the liner; winding a composite reinforcement around the liner while the support is disposed within the liner, wherein the composite reinforcement comprises glass and resin; curing the resin; retracting the support; and removing the mechanical support from the liner via the hole in the liner.

[0052] According to one or more of these embodiments, the lining comprises HDPE, PA-6, UHMWPE, or 316L stainless steel.

[0053] According to one or more embodiments of these examples, the composite reinforcement comprises at least 60% glass fiber and at least 10% resin.

[0054] According to one or more embodiments of these examples, the composite reinforcement comprises at least 10% insulator.

[0055] According to one or more embodiments of these examples, the insulator comprises perlite.

[0056] According to one or more embodiments of these examples, the composite reinforcement comprises a flame retardant.

[0057] According to one or more embodiments of these examples, the lining has an expansion joint.

[0058] According to one or more embodiments of these examples, the expansion joint includes a corrugated portion in the lining that facilitates the expansion and contraction of the lining.

[0059] According to one or more embodiments of these examples, the tank includes a cylinder that is elongated in the axial direction, and wherein an expansion joint facilitates the expansion and contraction of the liner in the axial direction.

[0060] According to one or more embodiments of these embodiments, the tank includes a cylinder that is elongated in an axial direction, and wherein the winding occurs when the axial direction is within 10° of the vertical orientation.

[0061] According to one or more embodiments of these embodiments, the winding includes: winding the liner using a first sublayer of glass-curing material and a first sublayer of resin; curing the first sublayer of resin; and winding a second sublayer of glass-curing material and a second sublayer of resin over the first sublayer of glass-curing material and the first sublayer of resin.

[0062] One or more embodiments provide an assembly for transporting compressed combustible gas, the assembly comprising: a vehicle; a storage space supported by the vehicle; a gas storage tank disposed within the storage space and defining an internal space, the storage tank having a pressure relief valve configured to release gas from the internal space into the insulated storage space if the pressure within the internal space exceeds a predetermined pressure; a compressed gas stored in the internal space of the storage tank; a gas sensor disposed within the storage space and configured to detect when the concentration of the gas in the storage space outside the storage tank exceeds a predetermined concentration; at least one fan connected to the storage space and configured to exchange air between the storage space and the surrounding environment around the vehicle; and a fan controller operatively connected to the gas sensor and the at least one fan, the fan controller being configured to increase the air exchange rate between the storage space and the surrounding environment in response to sensing that the gas concentration in the storage holder outside the storage tank exceeds a predetermined concentration.

[0063] According to one or more embodiments of these embodiments, the assembly includes a plurality of additional gas storage tanks disposed within a storage space, each of the plurality of additional gas storage tanks having an internal space and a pressure relief valve configured to release gas from the respective gas storage tank into the storage space if the pressure within the internal space of the respective gas storage tank exceeds a predetermined pressure.

[0064] According to one or more embodiments of these embodiments, the internal space of each of the plurality of storage tanks is fluidly isolated from each other.

[0065] According to one or more embodiments of these embodiments, the at least one fan includes at least one intake fan and at least one exhaust fan, the at least one intake fan being positioned to blow ambient air from the surrounding environment into the insulating storage holder, and the at least one exhaust fan being positioned to blow air from within the insulating storage holder to the surrounding environment.

[0066] One or more embodiments provide an assembly for transporting compressed combustible gas, the assembly comprising: a container defining a storage space; a compressed gas storage tank disposed within the storage space; a pressure relief valve connected to the tank to release pressurized gas stored in the tank when the valve is opened; and a temperature sensor attached to the container.

[0067] According to one or more embodiments of these embodiments, the temperature sensor includes: a linearly sealed conduit of at least 10 feet disposed within the storage space; a fluid disposed within the conduit; and a pressure sensor attached to the conduit for sensing when the pressure of the fluid within the conduit exceeds a predetermined pressure. According to one or more embodiments of these embodiments, the pressure sensor is operatively connected to a valve such that the valve opens in response to a pressure sensed by the pressure sensor exceeding a predetermined pressure.

[0068] According to one or more embodiments of these examples, the pressure sensor includes a rupture disc.

[0069] According to one or more embodiments of these examples, the container includes an ISO container.

[0070] One or more embodiments provide a double-walled safety hose comprising: an outer hose; an inner hose disposed inside the outer hose and configured to transfer pressurized fluid from a first end to a second end of the inner hose through an internal space; an outer space defined between the inner hose and the outer hose; and a pressure relief valve operatively connected to the outer space and configured to discharge fluid from the outer space if the pressure in the outer space exceeds a predetermined pressure.

[0071] According to one or more embodiments of these embodiments, the double-walled safety hose includes a ventilation channel having a first end and a second end, the first end of the ventilation channel being in fluid communication with the external space, and a pressure relief valve disposed in the ventilation channel.

[0072] According to one or more embodiments of these examples, the double-walled safety hose includes a compressor with an outlet, the compressor being fluidly connected to an external space and configured to deliver compressed fluid to the external space.

[0073] According to one or more embodiments of these embodiments, the compressor includes a pressure regulating compressor configured to sense pressure in an external space and to deliver compressed fluid to the external space when the sensed pressure in the external space drops below a set pressure.

[0074] According to one or more embodiments of these examples, the double-walled safety hose includes a fluid source operatively connected to the compressor inlet.

[0075] According to one or more embodiments of these examples, the pressure relief valve includes a single-use rupture disc.

[0076] According to one or more embodiments of these examples, the double-walled safety hose includes a gas sensor positioned to sense the presence of a gas in an external space through which the gas is delivered.

[0077] One or more embodiments provide a system for transmitting compressed gas. The system includes: a first channel having a first inlet and a first outlet, the first channel having a first rated pressure and an inner diameter of less than 2 inches; and a second channel having a second inlet and a second outlet, the second outlet being connected to the first channel via a flow control mechanism that prevents fluid from flowing from the first channel into the second channel, the second channel having a second rated pressure lower than the first rated pressure, and the second channel having an inner diameter of more than 2 inches. According to one or more embodiments of these embodiments, the flow control mechanism includes a check valve or a pressure regulating valve.

[0078] According to one or more embodiments of these embodiments, the flow control mechanism includes a pressure regulating valve disposed between a second outlet and a first channel, the pressure regulating valve being configured to close when the pressure in the first channel exceeds a predetermined pressure.

[0079] According to one or more embodiments of these embodiments, the system includes a check valve that separates the pressure regulating valve from the first channel.

[0080] According to one or more embodiments of these embodiments, the system includes an additional check valve disposed between the pressure regulating valve and the second outlet, the additional check valve preventing fluid from flowing from the pressure regulating valve into the second channel.

[0081] According to one or more embodiments of these embodiments, the system includes: a third channel extending from the second channel to the first channel, the third channel having a third inlet and a third outlet; and a compressor disposed along the third channel and configured to compress gas received from the second channel and deliver the resulting compressed gas to the first channel.

[0082] According to one or more embodiments of these embodiments, the system includes a check valve disposed in a third channel and preventing fluid from flowing from the first channel through the third channel into the second channel.

[0083] One or more aspects of these and / or other aspects of the various embodiments of the invention, as well as the operational methods and functions of the combination of related structural elements and barrels, and the economics of manufacture, will become more apparent after considering the following description and appended claims with reference to the accompanying drawings, all of which form a part of this specification, wherein the same reference numerals denote corresponding parts in the various drawings. In one embodiment, the structural components illustrated herein are drawn to scale. However, it should be clearly understood that the drawings are for illustrative and descriptive purposes only and are not intended to be construed as limiting the invention. Furthermore, it should be understood that structural features shown or described in any embodiment herein may be used in other embodiments. As used in the specification and claims, unless the context clearly specifies otherwise, the singular forms “a,” “an,” and “the” also include plural references.

[0084] All closed-end (e.g., between A and B) and open-end (greater than C) value ranges disclosed herein explicitly include all ranges falling within or nested within these ranges. For example, a disclosed range of 1 to 10 is understood to include, among other ranges, 2 to 10, 1 to 9, 3 to 9, etc. Similarly, where multiple parameters (e.g., parameter C, parameter D) are individually disclosed as having ranges, the embodiments disclosed herein explicitly include embodiments that combine any value within the disclosed range of one parameter (e.g., parameter C) with any value within the disclosed range of any other parameter (e.g., parameter D). Attached Figure Description

[0085] To better understand the various embodiments and other objects, and their further features, reference will be made to the following description, which will be used in conjunction with the accompanying drawings, wherein:

[0086] Figure 1 This is a schematic diagram of a split-flow gas cooling system 100 according to one or more embodiments.

[0087] Figure 2 This is a schematic diagram of a cryogenic compressed hydrogen transport vehicle according to one or more embodiments.

[0088] Figure 3 This is the hydrogen phase diagram.

[0089] Figure 4 This is a schematic diagram of a cryogenic compressed hydrogen transport vehicle according to one or more embodiments.

[0090] Figure 5 This is a cross-sectional view of a cryogenic compressed hydrogen storage tank according to one or more embodiments.

[0091] Figure 6This is a cross-sectional end view showing a manufacturing step during the manufacture of a cryogenic compressed hydrogen storage tank according to one or more embodiments.

[0092] Figure 7 This is a schematic diagram of an air exchange system used for storing compressed flammable or other hazardous gases.

[0093] Figure 8 This is a schematic diagram of a temperature sensor for a storage container according to one or more embodiments.

[0094] Figure 9 This is a cross-sectional view of the end of a double-walled hose according to one or more embodiments.

[0095] Figure 10 yes Figure 9 A schematic diagram of a double-walled flexible tube.

[0096] Figures 11 to 12 This is a schematic diagram of a dual-pressure gas transmission system according to different embodiments.

[0097] Figure 13 This is a schematic diagram of a split-flow gas cooling system 7000 according to one or more embodiments.

[0098] Figure 14 Is Figure 14 A schematic diagram of the refrigeration system 310b of the system 7000 shown.

[0099] Figure 15 This is a schematic diagram of a system 7500 for delivering hydrogen to a steel plant according to one or more embodiments.

[0100] Figure 16 This is a schematic diagram of the 8000 system used to generate cryogenic compressed hydrogen. Detailed Implementation

[0101] Split-flow gas cooling

[0102] like Figure 1 As shown, one or more embodiments provide a split-flow cooling system 100 and a method for splitting a first compressed gas flow 110 into a second compressed gas flow 120 and a third compressed gas flow 130, wherein the third flow 130 is used to cool the second compressed gas flow 120. The system trades a pressure drop in the third flow 130 for a temperature drop in the second flow 120, preferably without sacrificing pressure in the second flow.

[0103] like Figure 1As shown, compressed gas passage 200 extends from gas inlet 210 sequentially through connectors 300 and 330, through heat exchanger 280, through active cooler 310, and reaches distributor 220 (e.g., Y-connection or T-connection). Passage 230 sequentially exits distributor 220, passes through heat exchanger 270, and leads to cooler high-pressure gas outlet 240. Passage 250 extends from distributor 220 sequentially through expansion cooler 260, heat exchanger 270, heat exchanger 280, compressor 290, and finally returns to connector 300 in passage 200. Passage 320 leads from connector 330 to warm, high-pressure gas outlet 340.

[0104] In the illustrated embodiment, connector 330 is downstream of connector 300, but their relative positioning can be switched without departing from the scope of various embodiments.

[0105] The cooler 310 may include any type of active cooler (e.g., a phase change cooler based on Freon, HFA, or other refrigerants). The cooler 310 draws heat away from the gas flow 110 passing through channel 200 to cool the gas flow 110. However, according to various alternative embodiments, the cooler 310 may be omitted without departing from the scope of various embodiments of the invention.

[0106] In the illustrated embodiment, the cooler 310 cools the first stream 110. However, according to an alternative embodiment, the cooler may instead be disposed in the channel 230 between the splitter 220 and the heat exchanger 270 to cool the second stream.

[0107] exist Figure 1 In the illustrated embodiment, the cooler 310 is a single-stage cooler 310. However, according to an alternative embodiment, the cooler 310 may include a multi-stage cooler 310, such as... Figure 13 As shown. Figure 13 As shown, the cooler 310 includes a first-stage cooler 310a and a second-stage cooler 310b.

[0108] According to one or more embodiments and as follows Figure 13 As shown, the first-stage refrigerator 310a provides pre-cooling and cools the process fluid flow 110 to a temperature between -25℉ and -45℉. According to various embodiments, the refrigerator 310a may use a refrigerant such as propane in its coolant circuit.

[0109] According to one or more embodiments and as follows Figure 13As shown, the second-stage cooler 310b further cools the process fluid flow 110. According to one or more embodiments, the second-stage cooler 310b is a deep-cooling cycle cooler that cools the process fluid flow 110 to a temperature between -100℉ and -370℉. According to various embodiments, this two-stage cooling can help promote a process fluid temperature of approximately -320℉ at outlet 240.

[0110] like Figure 14 As shown, the refrigerator 310b may include a cooling circuit 7100. In the circuit 7100, refrigerant sequentially passes through a compressor 7110, a heat exchanger / refrigerator 7120, an expander 7130, and a heat exchanger 7140. The compressor 7110 compresses the refrigerant, which raises its temperature. The heat exchanger 7120 itself may be an active refrigeration system (e.g., an air or pre-cooling cycle) and is designed to remove heat from the refrigerant. The compressed and cooled refrigerant then passes through an expander that cools the refrigerant before it passes through the heat exchanger 7140, where heat is transferred from the process fluid stream 110 to the refrigerant in the circuit 7140, thereby cooling the process fluid stream 110.

[0111] According to various embodiments, control valves or other devices may be provided in any of the channels 200, 230, 250, 320, 380 to control the flow rate through these channels. Controlling the relative flow rates of different flows can help control the outlet temperature of the flows through heat exchangers 270, 280, thereby better matching the target temperature (e.g., the temperature of flow 120 at outlet 240).

[0112] According to various embodiments, the expansion cooler 260 may be, for example, an orifice, a turbine expander 260a (see...). Figure 13 ), or JT expander. If using turbine expander 260a (e.g. Figure 13 As shown), a turbo expander 260a can optionally be used to recover energy from the gas stream 130. According to one or more embodiments, the turbo expander 260a is used in embodiments where the JT expander would be inefficient or ineffective (e.g., if the temperature of the stream 130 passing through the cooler 260 causes the stream 130 to have a JT coefficient close to 0 or negative). According to various embodiments, the energy recovered from the expander 260a can be used to drive the compressor 290 and / or the compressor 7200 (see...). Figure 13Energy transfer from expander 260a to compressor(s) 290, 7200 can be achieved through mechanical connections (e.g., the output shaft of expander 260a is directly connected to the input shaft of compressor(s) 290, 7200 or via a gearbox or transmission) or electrical connections (e.g., by using the output shaft of expander 260a to drive a generator, the electricity generated by which is supplied to a motor that drives compressor(s) 280, 7200).

[0113] According to one or more embodiments, the expansion cooler 260 has a variable flow rate controlled by a temperature sensor (and / or a pressure sensor for assessing temperature) that senses the temperature of the second stream 120 downstream of the heat exchanger 270 (e.g., between the heat exchanger 270 and the outlet 240). According to various embodiments, the flow rate is automatically controlled to avoid overcooling. According to various embodiments, the temperature-controlled expansion cooler 260 is configured to increase the flow rate of the third stream 130 when the temperature in the second stream 120 downstream of the cooler 260 exceeds a predetermined temperature. Additionally and / or alternatively, the temperature-controlled expansion cooler 260 is configured to regulate the flow rate of the third stream 130 in order to maintain the temperature of the second stream 120 downstream of the cooler 260 within predetermined temperature parameters, such as: (a) at least -150℉, -125℉, -100℉, -90℉, -80℉, -70℉, -60℉, -50℉, -40℉, -30℉, -20℉, -10℉, and / or 0℉, (b) less than 40℉, 30℉, 20℉, 10℉, 0℉, -10℉, -20℉, -30℉, -40℉, -50℉, -60℉, -70℉, -80℉, -90℉, and / or -100℉, and / or (c) the temperature between any two such values ​​(e.g., between -150℉ and 40℉, between -60℉ and -40℉).

[0114] According to one or more embodiments, system 100 may optionally include a bypass channel 380 connected to channels 200 upstream and downstream of heat exchanger 280. A bypass valve 390 is disposed in channel 380. According to various embodiments, valve 290 is a temperature-controlled valve that selectively opens and closes based on a temperature sensor (not shown) that senses the temperature of a third stream 130 downstream of heat exchanger 280. According to various non-limiting embodiments, the temperature-controlled valve selectively opens to allow a portion of stream 110 to bypass the heat exchanger, thereby preventing overcooling of stream 110 (and downstream branch stream 130).

[0115] Channels 200, 230, 250, 320, and 380 may include any suitable type of channel for conveying gas at the temperature and pressure of the gas passing through such channel(s). The channel may be rigid (e.g., metal tube), flexible (e.g., hose), and / or a mixture of rigid and flexible channels.

[0116] Various inlets and outlets 210, 340, 240 may include detachable connectors, or may be connected to the gas source and destination in other ways (e.g., via welded joints, threaded joints, etc.).

[0117] In the following text, see references Figure 1 To describe the operation of system 100.

[0118] Inlet 210 is drawn from a source of compressed gas. According to various embodiments, the incoming source gas flow 350 received at inlet 210 has the following pressures: (1) at least 250 psig, 300 psig, 350 psig, 400 psig, 450 psig, 500 psig, 1000 psig, 1500 psig, 2000 psig, 2500 psig, 3000 psig, 3500 psig, 4000 psig, 4500 psig, 5000 psig, 6000 psig, 7000 psig, 8000 psig, 9000 psig, or 10000 psig. 11,000 psig, and / or 12,000 psig, (2) up to 14,000 psig, 12,000 psig, 10,000 psig, 8,000 psig, 6,500 psig, 5,000 psig, 4,500 psig, 4,000 psig, 3,500 psig, 3,000 psig, 2,000 psig, and / or 1,500 psig, and / or (3) any pressure between any two such values ​​(e.g., between 250 psig and 14,000 psig, between 1,500 psig and 4,500 psig). According to various embodiments, the source gas flow 350 has the following temperatures: (a) at least -40℉, -20℉, 0℉, 10℉, 20℉, 30℉, 40℉, 50℉, 60℉, 70℉, 80℉, 90℉, 100℉, 110℉, and / or 120℉, (b) less than 200℉, 190℉, 180℉, 170℉, 160℉, 150℉, 140℉, 130℉, 120℉, 110℉, 100℉, 90℉, 80℉, 70℉, 60℉, 50℉, 40℉, 30℉, 20℉, and / or 10℉, and / or (c) a temperature between any two such temperatures (e.g., between 0℉ and 200℉, between 60℉ and 150℉, between 80℉ and 140℉). According to various embodiments, a compressor (not shown) located upstream of inlet 210 can compress and heat the gas, resulting in the incoming source gas flow 350 having high pressure and high temperature.

[0119] According to one embodiment, the compressed gas received at inlet 210 is compressed natural gas (CNG). However, according to various alternative embodiments, the compressed gas received at inlet 210 may include any gas (e.g., air, nitrogen, argon, carbon dioxide) that has a positive JT coefficient as the gas flow 130 passes through the expansion cooler 260. According to alternative embodiments, the compressed gas contains hydrogen at a temperature below 200 K.

[0120] The incoming source stream 350 mixes with the third stream 130 at the connector 300 to form the first stream 110. Such mixing is preferred for embodiments where heat is extracted from the stream 130 between the compressor 290 and the connector 300 (e.g., via an active or passive refrigeration system (not shown) disposed in a passage between the compressor 290 and the connector 300). However, according to various alternative embodiments (not shown), the third stream 130 is never mixed back into the source stream 350, in which case the third stream 130 is not recirculated. Instead, the third stream 130 may alternatively flow to a low-pressure outlet.

[0121] According to various embodiments, a fourth stream 360 branches off from the connector 330 to provide high-pressure gas to the outlet 340. According to various embodiments, the fourth stream 360 includes a portion of the source stream 350 and a portion of the third stream 130 that has already been mixed with the source stream 350. According to one or more embodiments in which the third stream 130 does not mix back into the source stream 350, the fourth stream 360 may consist of a portion of the source stream 350.

[0122] According to various embodiments, the fourth stream 360 is supplied to the outlet 340 under the following conditions: i) the pressure is (1) at least 250 psig, 300 psig, 350 psig, 400 psig, 450 psig, 500 psig, 1000 psig, 1500 psig, 2000 psig, 2500 psig, 3000 psig, 3500 psig, 4000 psig, 4500 psig, 5000 psig. 1.5 psig, 6000 psig, 7000 psig, 8000 psig, 9000 psig, 10000 psig, 11000 psig and / or 12000 psig, (2) pressures up to 14000 psig, 12000 psig, 10000 psig, 8000 psig, 6500 psig, 5000 psig, 4500 psig, 4000 psig, 3500 psig, 3000 psig psig, 2000psig, and / or 1500psig, and / or (3) any pressure between any two such values ​​(e.g., between 250psig and 14000psig, between 1500 and 4500psig); and / or ii) temperatures of (a) at least -40℉, -20℉, 0℉, 10℉, 20℉, 30℉, 40℉, 50℉, 60℉, 70℉, 80℉, 90℉, 100℉, 110℉ and / or 120℉, (b) below 200℉, 190℉, 180℉, 170℉, 160℉, 150℉, 140℉, 130℉, 120℉, 110℉, 100℉, 90℉, 80℉, 70℉, 60℉, 50℉, 40℉, 30℉, 20℉ and / or 10℉, and / or (c) the temperature between any two such temperatures (e.g., between 0℉ and 200℉, between 60℉ and 150℉, between 80℉ and 140℉).

[0123] According to various embodiments, the first stream 110 enters the heat exchanger 280 at a higher temperature than the third stream 130. As a result, heat is transferred from the first stream 110 to the third stream 130 via the heat exchanger 280. According to one or more embodiments, the first stream 110 enters the heat exchanger 280 at approximately 120℉ and exits at 60℉. According to various embodiments, the third stream 130 enters the heat exchanger 280 at -20℉ and exits at 80℉. However, according to various embodiments, the heat exchanger 280 can be completely omitted.

[0124] After exiting the heat exchanger 280, the first stream 110 passes through a refrigeration unit 310, which cools the first stream 110. According to various embodiments, the refrigeration unit 310 cools the first stream 110 by: (a) at least 5℉, 10℉, 15℉, 20℉, 25℉, 30℉, 35℉, 40℉, 45℉, 50℉, 60℉, 70℉, 80℉, 90℉, 100℉, 110℉, 120℉, 130℉, 140℉, 150℉, 175℉, 200℉, 250℉, 300℉, and / or 350℉; (b) less than 500℉, 450℉, 400℉, 350℉, 300℉, 250℉. 200℉, 175℉, 150℉, 140℉, 130℉, 120℉, 110℉, 100℉, 90℉, 80℉, 75℉, 70℉, 65℉, 60℉, 55℉, 50℉, 45℉, 40℉, 35℉, 30℉, 25℉, 20℉, 15℉, 10℉, and / or 5℉, and / or (c) temperatures between any two such values ​​(e.g., between 5℉ and 500℉, between 15℉ and 50℉, between 100℉ and 400℉, between 200℉ and 500℉). However, according to various alternative embodiments, the refrigeration unit 310 is completely omitted. In such embodiments, active refrigeration can be omitted from the entire system 100.

[0125] After leaving the refrigeration unit 310, the first stream is split into a second stream 120 and a third stream 130 at the splitter 220. The second stream 120 then passes through a heat exchanger 270 that cools the second stream 120. The third stream 130 passes through an expansion cooler 260 that reduces both the pressure and temperature of the third stream 130, and then passes through the heat exchanger 270.

[0126] According to various embodiments, the expansion cooler 260 cools the third stream 130 by: (a) at least 5℉, 10℉, 15℉, 20℉, 25℉, 30℉, 35℉, 40℉, 45℉, 50℉, 55℉, 60℉, 65℉, 70℉, 75℉, 80℉, 85℉, 90℉, 95℉, and / or 100℉, (b) less than 110℉, 105℉, 100℉, 95℉, 90℉, 85℉, 80℉, 75℉, 70℉, 65℉, 60℉, 55℉, 50℉, 45℉, 40℉, 35℉, 30℉, 25℉, 20℉, 15℉, 10℉, and / or 5℉, and / or (c) between any two such values ​​(e.g., between 5℉ and 110℉, between 40℉ and 90℉).

[0127] The second stream 120 enters the heat exchanger 270 at a higher temperature than the third stream 130, so heat is transferred from the second stream 120 to the third stream 130, and the second stream 120 is cooled.

[0128] According to one or more embodiments, a third stream 130 enters heat exchanger 270 at -70℉ and exits at -20℉. According to various embodiments, a second stream 120 enters heat exchanger 270 at 0℉ and exits at -40℉ (e.g., for one or more embodiments where the process fluid is natural gas). The temperature at which the second stream enters heat exchanger 270 will depend particularly on other conditions such as whether the first stream 110 passes through heat exchanger 280 and / or refrigeration unit 310. In embodiments where heat exchanger 280 and refrigeration unit 310 are omitted and the third stream 130 is not remixed with source stream 350, the second stream 120 may enter heat exchanger 270 at approximately the same temperature and pressure as the source stream 350 entering system 100.

[0129] According to various embodiments, heat exchanger 270 cools second stream 120 by: (a) at least 5℉, 10℉, 15℉, 20℉, 25℉, 30℉, 35℉, 40℉, 45℉, 50℉, 55℉, 60℉, 65℉, 70℉, 75℉, 80℉, 85℉, 90℉, 95℉ and / or 100℉, (b) less than 110℉, 105℉, 100℉, 95℉, 90℉, 85℉, 80℉, 75℉, 70℉, 65℉, 60℉, 55℉, 50℉, 45℉, 40℉, 35℉, 30℉, 25℉, 20℉, 15℉, 10℉ and / or 5℉, and / or (c) between any two such values ​​(e.g., between 5℉ and 110℉, between 40℉ and 90℉).

[0130] After exiting the heat exchanger 270, the second stream 120 continues to flow toward the cooled compressed gas outlet 240. According to various embodiments, the second stream 120 reaches the outlet 240 at the following temperatures: i) temperatures of: (a) at least -500℉, -450℉, -400℉, -350℉, -330℉, -300℉, -250℉, -200℉, -150℉, -125℉, -100℉, -90℉, -80℉, -70℉, -60℉, -50℉, -40℉, -30℉, -20℉, -10℉, and / or 0℉, (b) less than 40℉, 30℉, 20℉, 10℉, 0℉, -10℉, -20℉, -30℉, -40℉, -50℉, -60℉, -70℉, -80℉, -90℉, -100℉, -150℉, -200℉, -250℉, -300℉, -310℉, -320℉, -330℉, -340℉, -350℉, and / or -370℉, and / or (c) the temperature between any two such values ​​(e.g., between -500℉ and 40℉, between -150℉ and 40℉, between -60℉ and -40℉, between -100℉ and -370℉); and / or ii) the pressure is: (1) At least 250 psig, 300 psig, 350 psig, 400 psig, 450 psig, 500 psig, 1000 psig, 1500 psig, 2000 psig, 2500 psig, 3000 psig, 3500 psig, 4000 psig, 4500 psig, 5000 psig, 6000 psig, 7000 psig, 8000 psig, 9000 psig, 10000 psig, 11000 psig and / or 12000 psig. psig, (2) up to 14000 psig, 12000 psig, 10000 psig, 8000 psig, 6500 psig, 5000 psig, 4500 psig, 4000 psig, 3500 psig, 3000 psig, 2000 psig, and / or 1500 psig, and / or (3) any pressure between any two such values ​​(e.g., between 250 psig and 14000 psig, between 1500 psig and 4500 psig).

[0131] According to various embodiments, the second stream 120 reaches the outlet 240 at the following temperatures: i) lower than the source stream 350 at the inlet 210 by the following temperatures: (a) at least 10℉, 20℉, 30℉, 40℉, 50℉, 60℉, 70℉, 80℉, 90℉, 100℉, 110℉, 120℉, 130℉, 140℉, 150℉, 160℉, 170℉, 180℉, 190℉, 200℉, 250℉, 300℉, 350℉, 400℉, 450℉, and / or 500℉, (b) less than 600℉, 500℉, 400℉, 350℉, 300℉, 250℉, 200℉, 190℉, 180℉, 170℉, 160℉, 150℉, 140℉, 130℉, 1 20℉, 110℉, 100℉, 90℉, 80℉, 70℉, 60℉ and / or 50℉, and / or (c) the temperature between any two such values ​​(e.g., cooler between 10℉ and 600℉); and / or (ii) the pressure of the source flow 350 at inlet 210 deviates from the pressure of the following: 5000psi, 4000psi, 3000psi, 2000psi, 1000psi, 900psi, 800psi, 700psi, 600psi, 500psi, 400psi, 300psi, 200psi, 100psi, 75psi, 50psi, 40psi, 30psi, 20psi, and / or 10psi.

[0132] In an embodiment that includes heat exchanger 280, the third stream 130 passes through heat exchanger 280 after leaving heat exchanger 270.

[0133] According to one or more embodiments, the third stream 130, after exiting the heat exchanger 280, may pass through a compressor 290, which compresses the third stream to a pressure at or near that of the source stream 350. The third stream 130 mixes with the source stream 350 at a coupling 300 after exiting the compressor 290. However, according to various embodiments, the compressor 290 and coupling 300 are omitted, such that the third stream 130 is no longer circulated but can be conveyed to a destination configured to use lower-pressure gas from the third stream 130. Additionally and / or alternatively, the passage for stream 130 may lead to the inlet of a main compressor located upstream of inlet 210, in which case the main compressor (not shown) will replace compressor 290. The main compressor can compress both the incoming fresh gas flow and the recirculated stream 130. In such embodiments, an active or passive refrigeration system may be positioned between the outlet and inlet 210 of the main compressor to remove heat from the gas flow before it enters inlet 210.

[0134] According to one or more embodiments, the second stream 120 can be cooled relative to the temperature of the source stream 350 without the use of the active cooling unit 310.

[0135] According to various embodiments, the second stream 120 can be cooled without a significant pressure drop in the second stream 120.

[0136] Figures 13 to 14 An alternative split-flow cooling system 7000 according to one or more embodiments is shown.

[0137] like Figure 13 As shown, compressor 7200 is disposed in passage 200 between inlet 210 and coupling 300 to further compress the incoming process fluid flow 350. Compressor 7200 overpressures gas flow 110.

[0138] like Figure 13 As shown, channel 200 branches downstream of compressor 290, with one branch leading to connector 300 and a second branch leading to channel 200 at a location between inlet 210 and compressor 7200. This allows for single-stage compression of the recirculated fluid using only compressor 290, or multi-stage compression of the recirculated fluid using two compressors 7200 and 290.

[0139] like Figure 13 As shown, an expansion cooler (e.g., turbine expander 7210 and / or JT expander 7220) is disposed in a passage 230 between heat exchanger 270 and outlet 240 to further cool flow 120 before it reaches outlet 240. According to one or more embodiments and as shown... Figure 13 As shown, if the expansion cooler includes both a turbine expander 7210 and a JT expander 7220, they can be arranged in parallel via the use of a parallel passage 7230. According to various embodiments, if the process fluid is hydrogen and its temperature is low enough to have a sufficiently positive JT coefficient, such that passing the flow 120 through the JT valve 7220 cools the flow 120. According to various non-limiting embodiments, if the temperature of the hydrogen process fluid flow 120 upon reaching the expansion cooler is below -250℉, then the JT valve 7220 is used.

[0140] According to various embodiments, the combined use of an upstream overpressure booster compressor 7200 and downstream expansion coolers 7210, 7220 enables system 7000 to provide a colder gas flow 120 at outlet 240 than in one or more embodiments without such overpressure. The additional use and / or alternative use of a multi-stage cooler 310 can facilitate further cooling to very low temperatures. These additional cooling methods are particularly well-suited for embodiments where the working fluid is very low-temperature hydrogen, as hydrogen advantageously exhibits a higher JT coefficient at very low temperatures.

[0141] According to one or more embodiments of system 7000, the second stream 120 enters heat exchanger 270 at 0℉ and exits heat exchanger 270 at -40℉ (e.g., for embodiments where the process fluid is natural gas). The temperature of the second stream entering heat exchanger 270 will depend particularly on other conditions such as whether the first stream 110 passes through heat exchanger 280 and / or refrigeration unit 310. In embodiments where heat exchanger 280 and refrigeration unit 310 are omitted and the third stream 130 is not remixed with source stream 350, the second stream 120 may enter heat exchanger 270 at approximately the same temperature and pressure as the source stream 350 entering system 100.

[0142] According to one or more embodiments of system 7000, wherein the process fluid is hydrogen and a multi-stage refrigeration system 310 is used, a first stream 110 exits a first-stage refrigeration unit 310a (e.g., a propane-based refrigeration unit) at about -40℉ and exits a second-stage refrigeration unit 310b (e.g., a nitrogen-based or mixed-refrigerant-based refrigeration unit) at about -320℉.

[0143] Cryogenic Compressed Hydrogen Transportation System and Method

[0144] One or more embodiments provide a more efficient and / or cheaper system for transporting hydrogen. By transporting hydrogen in a cryogenically compressed state, hydrogen can be advantageously transported at densities close to those of liquid hydrogen without the need for complex and expensive liquefaction plants. As explained below, according to various embodiments, glass-reinforced hydrogen storage containers facilitate the efficient storage of cryogenically compressed hydrogen because the glass in the container is stronger at cryogenically compressed hydrogen temperatures than glass at higher (e.g., ambient) temperatures. As explained below, according to various embodiments, a liquid nitrogen-based refrigeration system is used to cool and / or maintain the cryogenically compressed hydrogen at its cryogenic compression temperature, which can advantageously maintain the stored cryogenically compressed hydrogen at a temperature that provides a high density at the storage pressure of the cryogenically compressed hydrogen. According to various embodiments, the use of both glass-reinforced storage tanks and liquid nitrogen-based refrigeration systems can synergistically facilitate the cost-effective transport of high-density cryogenically compressed hydrogen.

[0145] As used in this article, the term “cryo” refers to a temperature of 230K and below.

[0146] like Figure 2 As shown, the vessel 1000 includes a hull 1010 and an insulating retainer 1020 supported by the hull 1010. A plurality of cryogenic compressed hydrogen storage tanks 1030 are disposed in the insulating space 1020a of the retainer 1020 and are supported by the hull 1010.

[0147] The retainer 1020 is cooled by a liquid nitrogen refrigeration system 1040, which supplies liquid nitrogen to a well 1050 at the bottom of the retainer 1020. Figure 2 As shown, the refrigeration system 1040 includes a nitrogen cooling / liquefaction system 1060, a gaseous nitrogen channel 1070, a liquid nitrogen channel 1080, and a nitrogen generator 1090. The gaseous nitrogen channel 1070 is used to transfer gaseous nitrogen from the insulating space 1020a within the holder 1020 to the liquefaction system 1060. The liquid nitrogen channel 1080 is used to transfer liquid nitrogen from the liquefaction system 1060 to the well 1050. The nitrogen generator 1090 is connected to the liquefaction system 1060 or the gaseous nitrogen channel 1070 to provide "make-up nitrogen" to the system 1040.

[0148] The cooling / liquefaction system 1060 may include any suitable system for cooling and liquefying nitrogen (e.g., an evaporative gas liquefaction system). According to various embodiments, system 1060 includes a series of compressors and intercoolers.

[0149] Nitrogen generator 1090 may include any suitable nitrogen generator. As is known in the art, the illustrated generator 1090 extracts nitrogen from ambient air. According to various embodiments, the nitrogen generator provides separated nitrogen to channel 1070, liquefaction system 1060, and / or insulating space 1020a, the separated nitrogen being 90+%, 91+%, 92+%, 93+%, 94+%, 95+%, 96+%, 97+%, 98+%, 99+%, 99.9+%, 99.99+%, and / or 99.999+% nitrogen.

[0150] According to various embodiments, the nitrogen generator 1090 includes a compressor and a pressure swing absorption device, the compressor being configured to compress ambient air from around the ship 100, and the pressure swing absorption device being configured to separate nitrogen from the compressed air. According to various embodiments, the use of this high-purity nitrogen advantageously reduces the amount of flammable oxygen present in the insulating space 1020a, which can help prevent fires and explosions within the insulating space 1020a of the retainer 1020.

[0151] According to various embodiments, the oxygen concentration in the liquid in well 1050 is low, but still higher than the gaseous oxygen concentration in the gaseous portion of the insulating space 1020a of retainer 1020. This may occur, for example, because oxygen has a higher boiling point than liquid nitrogen, so oxygen in space 1020a will tend to condense and collect in well 1050. This process can naturally remove gaseous oxygen from space 1020a to further reduce the risk of fire within space 1020a.

[0152] According to various embodiments, an oxygen sensor is disposed in well 1050 to sense the oxygen concentration within the liquid nitrogen in well 1050. If the sensed oxygen level in the liquid within well 1050 exceeds a predetermined minimum, the liquid in well 1050 can be purged (e.g., introduced into the surrounding environment), and fresh liquid nitrogen with less oxygen can be generated and pumped into space 1020a to reduce the overall oxygen concentration within space 1020a.

[0153] According to various alternative embodiments (e.g., in the case of storing inert or non-flammable liquids in (multiple) tanks 1030), liquid air can be used instead of liquid nitrogen to cool space 1020a.

[0154] exist Figure 2 In the illustrated embodiment, channel 1080 delivers liquid nitrogen directly into well 1050. However, according to an alternative embodiment, channel 1080 may instead spray liquid nitrogen from above into space 1020a, which may help ensure a cooler and / or more uniform temperature throughout space 1020a.

[0155] According to various embodiments, the nitrogen generator 1090 may be omitted (e.g., if there is already enough liquid nitrogen available in well 1050).

[0156] System 1040 (including liquefaction system 1060, nitrogen generator 1090, and channels 1070 and 1080) is entirely mounted to or otherwise supported by vessel 1000. According to various alternative embodiments, nitrogen generator 1090 may alternatively be detached from vessel 1000 and connected only intermittently to vessel 1000 and system 1040 to provide supplemental nitrogen as needed (e.g., at a port). In such embodiments, nitrogen generator 1090 may be a land-based fixed system.

[0157] Well 1050 is a recess at the bottom of the insulating space 1020a within the retainer 1020, and serves to collect and concentrate the liquid nitrogen in the space 1020a. Well 1050 reduces the sloshing of the liquid nitrogen and tends to reduce the likelihood of damage to the insulation (e.g., foam) of the insulating retainer 1020 caused by excessive sloshing of the liquid nitrogen during the rolling motion of the ship 1000 due to waves. According to various embodiments, the bottom plate of the insulating space 1020a may include a baffle that further prevents the sloshing of nitrogen within the retainer 1020.

[0158] During operation, system 1040 ensures that a certain volume of liquid nitrogen is retained in well 1050. The insulated space 1020a is maintained at or near atmospheric pressure (e.g., between 0 and 0.1 psig or 15 psig relative to the ambient pressure outside the vessel 1000). According to various embodiments, the pressure within the insulated space 1020 is maintained by a liquefaction system 1040, which receives gaseous nitrogen from the insulated space 1020a as needed to ensure that the pressure within the insulated space 1020a remains within a desired range (e.g., between 0 and 15 psig or 0 and 0.1 psig relative to the ambient pressure around the vessel 1000). Consequently, when the liquid nitrogen in space 1020a evaporates into gaseous nitrogen, system 1040 receives and reliquefies the gaseous nitrogen. This selective reliquefaction process allows system 1040 to control the pressure within space 1020a. By controlling the vaporization rate of liquid nitrogen in space 1020a, the pressure within space 1020a is controlled, and thus the temperature within space 1020a is also controlled.

[0159] like Figure 2 As shown, according to various embodiments, a ventilation duct 1100 extends between an insulating space 1020a and the surrounding environment 1120 outside the vessel 1000. A pressure relief valve 1110 in the duct 1100 is configured to release gas from the insulating space 1020a to the surrounding environment 1120 if the pressure in the insulating space 1020a exceeds a predetermined pressure, for example (a) at least 0.001 psig, 0.1 psig, 0.5 psig, 2 psig, and / or 15 psig relative to the pressure in the surrounding environment 1120 outside the vessel 1000, (b) less than 15 psig, 10 psig, 5 psig, 2 psig, 1 psig, and / or 0.1 psig, and / or (c) at a set point between any two such values ​​(e.g., a predetermined pressure between 0.001 psig and 15 psig). According to various embodiments, the passage 1100 and valve 1110 may include an emergency blast hatch that separates the insulating space 1020a from the surrounding environment 1120 outside the vessel 1000.

[0160] According to various embodiments, the insulating space 1020a is almost entirely filled with gaseous nitrogen, which helps to suppress fire or explosion in the insulating space 1020a by essentially depriving the space 1020a of oxygen.

[0161] Liquid nitrogen in well 1050 and insulating space 1020a keeps insulating space 1020a relatively cool. The liquid nitrogen evaporates as needed to maintain the coolness of space 1020a. The liquid nitrogen stored in well 1050 and insulating space 1020a also acts as a thermal mass buffer, temporarily keeping insulating space 1020a cool even if system 1040 is shut down or malfunctions. Therefore, the liquid nitrogen stored in insulating space 1020a can delay or prevent an emergency that might otherwise occur if the temperature within insulating space 1020a rises, causing the temperature and / or pressure within tank 1030 to approach its rated / permissible maximum temperature and / or pressure.

[0162] According to various embodiments, the insulation retainer 1020 and the cooling system 1040 provide insulation space 1020a and / or internal space 1030a within the tank 1030 (see...). Figure 5 The temperature T is maintained at approximately -321 degrees Fahrenheit, close to the atmospheric pressure of liquid nitrogen. According to various embodiments, this temperature T is (a) at least -352℉, -350℉, -330℉, -325℉, and / or -320℉, (b) less than or equal to -20℉, -40℉, -60℉, -80℉, -82℉, -100℉, -140℉, -200℉, -240℉, -280℉, -310℉, and / or -315℉, and / or (c) between any two such values ​​(e.g., between -352℉ and -20℉, between -321℉ and -280℉, between -321℉ and -300℉). Figure 3 As shown, this low-temperature storage environment within the insulating space 1020 facilitates high-density hydrogen storage, particularly at pressures suitable for tank 1030.

[0163] According to various embodiments, during transport on ship 1000, the pressure of hydrogen in tank 1030 is (1) at least 250 psig, 300 psig, 350 psig, 400 psig, 450 psig, 500 psig, 600 psig, 700 psig, 800 psig, 900 psig, 1000 psig, 1500 psig, 2000 psig, 2500 psig, 3000 psig, 3500 psig, 4000 psig, 4500 psig, 5000 psig, 6000 psig, 7000 psig, 8000 psig, 9000 psig, 10000 psig, 110 00 psig, and / or 12000 psig, (2) up to 14000 psig, 12000 psig, 10000 psig, 8000 psig, 6500 psig, 5000 psig, 4500 psig, 4000 psig, 3500 psig, 3000 psig, 2000 psig, 1500 psig, 1250 psig, and / or 1000 psig, and / or (3) any pressure between any two such values ​​(e.g., between 250 psig and 14000 psig, between 900 psig and 10000 psig, between 1500 psig and 4500 psig).

[0164] According to various embodiments, the density of hydrogen in tank 1030 is (a) at least 1.0 lbm / ft. 3 1.5lbm / ft 3 2.0 lbm / ft 3 2.5 lbm / ft 3 3.0 lbm / ft 3 3.5 lbm / ft 3 4.0 lbm / ft 3 4.5 lbm / ft 3 5.0 lbm / ft 3 5.5 lbm / ft 3 and / or 6.0 lbm / ft 3 (b) Less than or equal to 6.0 lbm / ft 3 5.5 lbm / ft 3 5.0 lbm / ft 3 4.5 lbm / ft 3 4.0 lbm / ft 3 3.5 lbm / ft 3 3.0 lbm / ft 3 2.5 lbm / ft 32.0 lbm / ft 3 and / or 1.5 lbm / ft 3 And / or (c) the density between any two such values ​​(e.g., at 1.0 lbm / ft). 3 and 6.0 lbm / ft 3 Between, within 1.0 lbm / ft 3 and 5.5 lbm / ft 3 Between, at 3.0 lbm / ft 3 and 5.0 lbm / ft 3 Between, at 3.5 lbm / ft 3 and 5.0 lbm / ft 3 between).

[0165] The total number and size of the cans 1030 may depend on the size of the insulating space 1020a and the vessel 1000. According to various embodiments, the vessel's retainer 1020 and its insulating space 1020a may accommodate (a) at least 10, 50, 100, 200, 300, 400, and / or 500 cans 1030, (b) less than 1000, 900, 800, 700, 600, 500, 400, 300, 200, 100, 50, and / or 10 cans 1030, or (c) any number between any two such numbers (e.g., between 10 and 1000 cans 1030, between 50 and 500 cans). According to various embodiments, the total volumetric capacity of the combination of multiple cans 1030 in the insulating space 1020 is (a) at least 35 ft. 3 50 ft 3 75 ft 3 100 ft 3 250ft 3 500 ft 3 750 ft 3 1000 ft 3 5000 ft 3 10,000 ft 3 25,000 ft 3 50,000 ft 3 100,000 ft 3 200,000 ft 3 300,000 ft 3 400,000 ft 3 500,000 ft 3 600,000 ft 3 700,000 ft 3 800,000 ft3 900,000 ft 3 and / or 1,000,000 ft 3 (b) Less than 1,000,000 ft 3 750,000 ft 3 500,000 ft 3 250,000 ft 3 100,000 ft 3 50,000 ft 3 40,000 ft 3 30,000 ft 3 20,000 ft 3 10,000 ft 3 5000 ft 3 2500ft 3 1000 ft 3 500 ft 3 250 ft 3 100 ft 3 75 ft 3 and / or 50 ft 3 And / or (c) the volumetric capacity between any two such values ​​(e.g., in 35 ft). 3 and 1,000,000 ft 3 between).

[0166] In the illustrated embodiment, the retainer 1020 and the insulating space 1020a are sized to store multiple cans 1030. However, according to an alternative embodiment, the retainer 1020 and the space 1020a can be sized to accommodate a single can 1030.

[0167] According to various embodiments, the retainer 1020 may include any suitable thermal insulator (e.g., foam, dead space, etc.) to thermally insulate the space 1020a.

[0168] Although Figure 2 The cryogenic compressed hydrogen transport vehicle is illustrated as vessel 1000, but without departing from the scope of the invention, this vehicle can alternatively be any other suitable vehicle (e.g., barge, combination of one or more railcars, wheeled vehicle, ISO container, and semi-trailer, etc.). Similarly, although Figure 2 The storage container 1020 and storage space 1020a defined by the ship's retaining elements are shown, but the container 1020 may alternatively be any other suitable type of container (e.g., ISO container, railcar, etc.) without departing from the scope of the invention.

[0169] Liquid nitrogen replacement

[0170] According to various embodiments, liquid nitrogen can be stored within the insulating space 1020a, (a) outside the tank 1030, (b) within the internal space 1030a of the tank 1030, and / or (c) both inside and outside the tank 1030. According to various embodiments, liquid nitrogen is used as a displacement / ballast within the tank 1030 to facilitate the substantially isothermal and isobaric transfer of cryogenic compressed hydrogen into and out of the tank 1030.

[0171] According to various embodiments, liquid nitrogen is used as a displacement / ballast in a manner similar to that of the hydraulic fluid used in WO 2018 / 144328, the entire contents of which are incorporated herein by reference.

[0172] like Figure 4 As shown, the liquid nitrogen replacement system 1500 is supported by the vessel 1000. The system 1500 includes a liquid nitrogen storage container 1510, which is operatively connected via a liquid nitrogen channel 1520 to the interior space 1030a of one or more tanks 1030, and the liquid nitrogen channel 1520 is fluidly connected to a liquid port 1580 leading to the interior space of the tank 1030. Parallel within channel 1520 are: a pump 1530, an optional pump 1540, and a pressure regulating valve 1550. The pump 1530 is used to pump liquid nitrogen from storage container 1510 to tank(s) 1030; the optional pump 1540 is used to pump liquid nitrogen from tank(s) 1030 to storage container 1510; and the pressure regulating valve 1550 allows liquid nitrogen to flow from tank(s) 1030 to storage container 1510 when the pressure in tank(s) 1030 exceeds a predetermined value (e.g., the value is at or slightly above the desired tank 1030 pressure P).

[0173] According to various embodiments, pumps 1530 and 1540 are replaced by a single reversible pump, which is arranged in line with (i.e., arranged sequentially along the channel) or parallel to valve 1550.

[0174] According to various embodiments, tank 1030 is under a much higher pressure than storage container 1510 (e.g., if storage container 1510 is maintained at low pressure or ambient pressure). When flow in this direction is generated by using pump 1540 (or a reversible pump), the pressure difference may tend to cause liquid nitrogen to flow rapidly from tank 1030 to storage container 1510. According to various embodiments, pump 1540 (or a reversible pump) acts as a dynamic brake to slow, cool, and control the movement of liquid nitrogen from high-pressure tank 1030 back to low-pressure storage container 1510. Pump 1540 may be combined with a generator or other mechanical or electrical components that can recover the energy generated by this braking effect as liquid nitrogen is driven by the pressure difference through pump 1540 (or the reversible pump) and into container 1510.

[0175] According to various embodiments, liquid nitrogen can be supplied to storage container 1510 from any suitable source (e.g., nitrogen liquefaction system 1060, well 1050, etc.).

[0176] According to various embodiments, the liquid nitrogen storage container 1510 may be disposed within the insulating space 1020a. According to various embodiments, the well 1050 may be the storage container 1510 (preferably in embodiments where hydrogen is effectively isolated or separated from the liquid nitrogen used by the system 1500 when the liquid nitrogen is not in the tank(s) 1030). Alternatively, the liquid nitrogen storage container 1510 may be supported by the vessel 1000 but disposed outside the insulating space 1020a. If the container 1510 is stored outside the insulating space 1020a, then the container 1510 may be an insulating container. If the container 1510 is stored within the insulating space 1020a, the insulator may be omitted, allowing the liquid nitrogen in the container 1510 to contribute to the cooling of the insulating space 1020a.

[0177] Before loading tank 1030 with cryogenic compressed hydrogen, liquid nitrogen is pumped from storage container 1510 into the internal space 1030a of tank 1030 by pump 1530 to fill tank 1030. For loading tank 1030, cryogenic compressed hydrogen is delivered into tank 1030 via hydrogen channel 1560, which is fluidly connected to a gas port 1570 leading to the internal space 1030a of tank 1030. The incoming cryogenic compressed hydrogen preferably arrives at tank 1030 at a temperature T approximately equal to or close to the temperature T of the insulating space 1020a and at a preferred storage pressure P. Pressure regulating valve 1550 is configured to allow nitrogen to flow from tank 1030 to storage container 1510 when the pressure inside tank 1030 exceeds pressure P. Therefore, as cryogenic compressed hydrogen is loaded into tank 1030, liquid nitrogen is discharged from tank 1030, making the hydrogen loading process substantially isothermal and isobaric.

[0178] In order to transfer cryogenic compressed hydrogen from tank 1030, liquid nitrogen is pumped from storage container 1510 to the interior space 1030a of tank 1030 by pump 1530 at a rate substantially matched to the rate at which cryogenic compressed hydrogen leaves tank 1030 via channel 1560, so that the unloading process is substantially isothermal and isobaric.

[0179] When tank 1030 is not used to store cryogenic compressed hydrogen, any liquid nitrogen in tank 1030 can be pumped from tank 1030 to storage container 1510 via pump 1540. This process allows unused tank 1030 to be exposed to ambient pressure. According to various embodiments, compressor 1540 is completely omitted.

[0180] According to various embodiments, when tank 1030 is not used but is filled with liquid nitrogen, gaseous nitrogen can be injected into tank 1030 at or near pressure P in order to displace liquid nitrogen from tank 1030 to storage container 1510 via channel 1520 and valve 1550.

[0181] According to various embodiments, during loading cycles, unloading cycles, and / or when not used for storing cryogenic compressed hydrogen, tank 1030 is maintained at or near pressure P and temperature T. By maintaining tank 1030 at or near pressure P and cryogenic temperature T throughout its use, tank 1030 undergoes reduced pressure cycling, temperature cycling, pressure-based expansion / contraction, and / or temperature-based expansion / contraction, which results in less fatigue of tank 1030 and a longer service life.

[0182] In the illustrated embodiment, the gas port of the can 1030 is located at or near the top of the can 1030, while the liquid port 1580 is located at or near the bottom of the can 1030 (relative to gravity orientation). According to various embodiments, the liquid port leads to the bottom of the internal space 1030a by penetrating the bottom of the can 1030. Alternatively, as... Figure 5 As shown, the liquid port 1580 can be fluidly connected to the bottom of the internal space 1030 by penetrating the top of the tank 1030 and extending via the pipe / channel 1580a to the bottom of the internal space 1030a of the tank 1030.

[0183] Cryogenic compressed hydrogen is lighter than compressed nitrogen or liquid nitrogen; therefore, cryogenic compressed hydrogen will tend to float towards port 1570 and rise to the top of tank 1030, while nitrogen will tend to sink towards port 1580 and rise to the bottom. Figure 5 As shown, according to various embodiments, in order to further prevent the mixing of hydrogen and nitrogen within the internal space 1030a, a baffle 1600 is disposed within the internal space 1030a. For example... Figure 5As shown, baffle 1600 may include one or more horizontal structures within the interior space that slow down the vertical movement of fluid within the interior space. Additionally and / or alternatively, baffle 1600 may include a mesh (e.g., an expanded metal sheet) or other suitable structure.

[0184] According to various embodiments, such as Figure 5 As shown, a nitrogen / liquid sensor 1610 can be disposed in port 1570 to sense liquid nitrogen. This sensor 1610 is operatively connected to a sensor control valve 1600 in channel 1560 (see [reference]). Figure 4 When sensor 1610 senses nitrogen / liquid, sensor 1610 closes valve 1600. As a result, sensor 1610 and valve 1600 prevent nitrogen flow through hydrogen channel 1560. Similarly, gas / hydrogen sensor 1620 is disposed in port 1580 to sense hydrogen / gas. Sensor 1620 is operatively connected to sensor control valve 1590 in channel 1520 (see [link to sensor control valve]). Figure 4 The sensor 1620 and valve 1590 are configured to close valve 1590 when hydrogen is sensed. As a result, sensor 1620 and valve 1590 can be closed to prevent hydrogen from escaping from tank 1030 through channel 1520. Sensors 1610 and 1620 can be used to sense when hydrogen loading and unloading cycles have been completed for the associated tank 1030, respectively.

[0185] As a supplement to or alternative to the use of baffle 1600, a floating structure can be disposed in the internal space 1030a, and the density of the floating structure is between the density of the cryogenic compressed hydrogen in tank 1030 and the density of the liquid nitrogen in tank 1030a. The float is capable of vertical movement within the internal space 1030a of tank 1030. Therefore, the float will tend to float above the liquid nitrogen and sink below the cryogenic compressed hydrogen, which will tend to keep the hydrogen and nitrogen separated. Additionally and / or alternatively, a sensor can be added to sense the position of the float. As a supplement to or alternative to the sensors 1610 and / or 1620 discussed above, such a float sensor can be used to sense when tank 1030 is loaded with or unloaded with cryogenic compressed hydrogen. The float sensor can be operatively connected to valves 1590 and 1600 to close valve 1600 when the hydrogen unloading cycle is completed, and / or close valve 1520 when the hydrogen loading cycle is completed.

[0186] Storage tank 1030

[0187] According to various embodiments, the tank 1030 includes a glass-reinforced tank 1030 wound within glass (e.g., glass fiber). The reinforced glass is stronger at a lower temperature T within the insulating space 1020a than at a higher temperature (e.g., 273 K). Please refer to the Rockwell Corporation paper published in Glass Composites in 1968. This temperature-dependent property of glass makes it particularly suitable for reinforcing the tank 1030 of the ship 1000. The lower temperature T within the insulating space 1020a synergistically (a) reduces the temperature of hydrogen, which increases the density of hydrogen and the amount of hydrogen that can be transported on the ship 100, and (b) increases the strength of the glass-reinforced tank 1030. The low-temperature strength of the reinforced glass enables (a) the tank 1030 to be kept at higher pressures (and thus enables each vessel 1000 to store more hydrogen) and / or (b) the tank 1030 to use less reinforcing material, and is therefore cheaper and / or lighter.

[0188] According to various embodiments, such as Figure 5 As shown, tank 1030 includes a composite reinforcement 1030b disposed outside liner 1030c. According to various embodiments, composite reinforcement 1030b comprises a mixture of glass (e.g., fiberglass strands) and resin. According to various embodiments, liner 1030c comprises HDPE (e.g., 8 mm thick), PA-6 nylon (e.g., 0.2 mm thick), UHMWPE (e.g., 8 mm thick), or 316L stainless steel (e.g., 0.1 mm thick).

[0189] According to various embodiments, the glass-strengthened tank 1030 is cooled to temperature T before being pressurized, so as to utilize the higher glass strength of the tank at a lower temperature before pressurizing the tank 1030.

[0190] like Figure 4 As shown, gas port 1570 and / or passage 1560 include a pressure relief valve 1650, which can be connected to another ventilation passage 1660 to discharge pressurized gas from inside tank 1030 to a safe location outside retainer 1020 (e.g., ambient environment 1120 around vessel 1000). According to various embodiments, valve 1650 is incorporated into tank 1030 itself, or alternatively may be incorporated into passage 1560 which is in fluid communication with the internal space 1030a of tank 1030. Pressure relief valve 1650 can be any type of suitable valve (e.g., pressure regulating valve, emergency rupture valve / panel, overflow valve, etc.) that opens in response to the pressure in the internal space 1030a of tank 1030 exceeding a predetermined pressure (e.g., the rated pressure of tank 1030).

[0191] According to various embodiments, and as Figure 6 As shown, the canister 1030 is made by: (1) inserting the expandable instrument holder 1800 through the hole 1030d in the liner 1030c (see Figure 5 (2) Radially expanding the support 1800 within the internal space 1030a inside the liner 1030c to form a hoop shape that mechanically supports the liner 1020b in its appropriate shape (e.g., a generally cylindrical shape with rounded apexes) during the manufacturing process; (3) Wrapping the liner 1020c supported by the support with a composite layer 1030b containing uncured resin; (4) Allowing the resin to solidify; (5) Closing the support 1800; (6) Removing the closed support 1800 from the liner 1030c through the hole 1030d; and (7) Attaching the port 1570 and / or the port 1580 to the hole 1030d in the liner 1020c to form the internal space 1030a, which is sealed except for the port 1570 and / or the port 1580. According to various embodiments, the baffle 1600 and / or the tube 1580a may be inserted into the interior space 1030a prior to step (7). Depending on the size of the hole 1030d, the baffle 1600 may be a retractable baffle 1600 that is retracted to fit through the hole 1030d and then expands within the interior space 1030a (e.g., similar to how the mast and sail are raised in a "ship-in-a-bottle").

[0192] Unlike the airbags that can be used to support the liner 1030c during winding, the support 1800 is not inflatable. Instead, it expands and contracts by relying on the relative movement between the plates of the support 1800 (e.g., a four-bar linkage).

[0193] The bracket 1800 can be fully retracted to fit through hole 1030d (see...). Figure 5 And then it can be expanded within the liner 1030c to mechanically support the liner 1030c during steps (3) to (4) discussed above. For example, according to various embodiments, a plurality of axially spaced rings can be inserted into the bore 1030d while the rings are closed, and then expanded within the can to provide structural support. For example, according to various embodiments, each ring expands like an umbrella (e.g., via a series of interconnected four-bar linkages or other mechanical mechanisms to facilitate expansion, via a pneumatic bladder, via a screw expansion mechanism similar to a gear-expansion corkscrew).

[0194] According to various embodiments, the winding step (3) occurs when the liner 1030c is configured in a substantially vertical orientation (i.e., the elongated axes 1810 of the liner 1030c and the can 1030 are pointing substantially vertically). According to various embodiments, the winding step (3) occurs when the elongated axis 1810 of the liner 1030c is within a vertical range of 20°, 15°, 10°, and / or 5°. This vertical winding can help prevent the liner 1030c from sagging during winding.

[0195] According to various embodiments, the composite layer 1030b is wound around the liner 1030c in multiple stages, allowing the resin to cure between each winding stage. As a result, the initially cured sublayer of the composite layer 1030b provides mechanical reinforcement to the liner 1030c during subsequent winding with additional composite reinforcing sublayers. According to various embodiments, the multi-stage winding process avoids any need for the use of a support 1800 or other internal reinforcement structures (e.g., inflatable airbags). According to various embodiments, the composite layer 1030b is wound around the liner 1030c in at least two, three, and / or four stages, with the resin curing between each stage. According to various embodiments, the first sublayer of the composite layer 1030b is thinner and lighter than subsequent sublayers. In such embodiments, the strength of the first sublayer helps maintain the shape of the liner 1030c when subsequent, heavier sublayers of the composite layer 1030b are added.

[0196] According to various embodiments, the composite reinforcing layer 1030 comprises (a) at least 30%, 40%, 50%, and / or 60% by weight of glass fiber, (b) less than or equal to 90%, 80%, 70%, and / or 60% by weight of glass fiber, and / or (c) glass fiber between any two such values ​​(e.g., 30% to 90% by weight of glass fiber). According to various embodiments, the composite layer 1030b comprises (a) at least 1%, 2%, 3%, 4%, 5%, 6%, 7%, 8%, 9%, 10%, 15%, and / or 20% by weight of resin, (b) less than or equal to 50%, 40%, 30%, 25%, 20%, 15%, and / or 10% by weight of resin, and / or (c) resin between any two such values ​​(e.g., 1% to 50% by weight of resin, 10% to 20% by weight of resin).

[0197] According to various embodiments, composite layer 1030b further includes (a) at least 1%, 2%, 3%, 4%, 5%, 6%, 7%, 8%, 9%, 10%, 15%, and / or 20% by weight of an insulator, (b) less than or equal to 50%, 40%, 30%, 25%, 20%, 15%, and / or 10% by weight of an insulator, and / or (c) an insulator between any two such values ​​(e.g., 1% to 50% by weight of an insulator, 10% to 20% by weight of an insulator). According to various embodiments, the insulator may comprise any suitable insulator (e.g., a flame-retardant insulator such as perlite). According to various embodiments, composite layer 1030b is a flame retardant (e.g., via a flame-retardant compound (e.g., magnesium oxide) added to the resin / composite mixture, via a non-mechanical additional layer, and, if a combination of insulator and refractory material is required, this additional layer may be made of mineral wool, chopped glass fiber (w / o resin), or perlite.

[0198] like Figure 5 As shown, the liner 1030c may include one or more expansion joints 1030e. The expansion joint 1030e extends around the circumference of the liner 1030c and allows the liner 1030c to expand and contract axially (e.g., Figure 5 (shown upwards and downwards). According to various embodiments, the expansion joint 1030e includes one or more corrugations, accordion pleats, or other undulations in the liner 1030c. These expansion joints 1030e enable the liner 1030c to expand and contract axially during use in response to changes in temperature and / or pressure within the tank 1030.

[0199] ventilation control

[0200] like Figure 7 As shown, the insulated storage holder 1020 may have an inlet vent 2000 and an outlet vent 2010, as well as associated inlet fans 2020 and outlet fans 2030. The vents 2000 and 2010 may be louvered vents that automatically open when fan 2020 or fan 2030 is turned on and automatically close when fan 2020 or fan 2030 is turned off. In embodiments where the holder 1020 is cooled, the vents 2000 and 2010 and fans 2020 and 2030 may be used only when necessary to expel potentially explosive or other hazardous gases (e.g., hydrogen) from the insulated space 1020a.

[0201] According to alternative embodiments (including such Figure 7In the illustrated embodiment, retainer 1020 and space 1020a are not cooled and / or insulated. In such an embodiment, the temperature and pressure within space 1020a can be substantially the same as the surrounding environment 1120 outside the vessel 1000. In such an embodiment, fans 2020, 2030 can operate continuously to continuously ventilate space 1020a at a desired air exchange rate (ACH).

[0202] like Figure 7 As shown, the gas port 1570 of each of the tanks 1030 can be connected to a common gas passage 1560 via a corresponding isolation valve 2040 disposed outside the respective tank 1030. The valve 2040 can be selectively closed to isolate the fluid stored in each tank 1030 from other tanks 1030 and space 1020a (e.g., in the event of a leak in one or more tanks 1030 or associated passage).

[0203] like Figure 7 As shown, one or more gas sensors (e.g., hydrogen sensors) 2050 may be disposed in space 1020a to sense the presence of combustible gases (e.g., hydrogen leaking from (multiple) tanks 1030) or other hazardous gases (e.g., if hazardous gases are stored in tank 1030).

[0204] like Figure 7 As shown, one or more temperature sensors 2060 may be disposed in space 1020a to sense the temperature within space 1020a.

[0205] like Figure 7 As shown, the electronic controller 2070 is operatively connected (e.g., via wired or wireless communication) to valve 2040, fans 2020, 2030 and sensors 2050, 2060 to control fans 2020, 2030 and valve 2040 based on sensing parameters from sensors 2050, 2060.

[0206] According to various embodiments, controller 2070 may include any suitable analog or digital controller (e.g., a personal computer with A / D input / output capability) configured to receive signals from sensors 2050, 2060 and send control signals to fans 2020, 2030 and valve 2040 to control the operation and / or flow rate of fans 2020, 2030 and to close (or open) valve 2040.

[0207] According to various embodiments where space 1020a is maintained near ambient temperature (rather than at a cooling / low temperature), controller 2070 controls fans 2020, 2030 to provide a predetermined number of ACH (air changes per hour). Controller 2070 can control ACH by operating one, more, or all of fans 2020, 2030 intermittently at a relatively high flow rate or continuously at a relatively low flow rate. According to various embodiments, controller 2070 can be programmed to increase ACH in response to a sensed temperature in space 1020a exceeding a predetermined value(s). According to various embodiments, controller 2070 is programmed to increase ACH to at least a predetermined value in response to a sensed concentration of leaked gas (e.g., CNG, hydrogen) in space 1020a exceeding a threshold concentration. According to various embodiments, controller 2070 is configured to dynamically control the ACH value to ensure that the sensed concentration of combustible gas in space 1020a remains below the lower explosive limit (LEL) concentration. According to various embodiments, the controller 2070 is programmed to close the valve 2040 and isolate the tanks 1030 from each other in response to sensing that the concentration of combustible gas in space 1020a is higher than a predetermined value.

[0208] The controller’s ability to keep space 1020a below LEL is useful in embodiments where the pressure relief valve 1650 of tank 1030 may discharge gas from overpressure tank 1030 into space 1020a (i.e., in embodiments where the pressure relief valve does not discharge into the surrounding environment 1120).

[0209] According to various embodiments, the temperature sensor 2060 for sensing the temperature in space 1020a and / or tank 1030 includes a thermometer. For example... Figure 8As shown, temperature sensor 2060 can be replaced by a pressure-based temperature sensor 3000. Sensor 3000 includes a sealed conduit 3010 within space 1020a, pressure sensor 3020, and fluid 3030 disposed within conduit 3010. The path of conduit 3010 can be three-dimensional. Conduit 3010 can extend along the periphery of space 1020a (e.g., along all six dimensions or all eight edges of box-shaped space 1020a (e.g., if space 1020a is defined by ISO container 1020)). In the illustrated embodiment, conduit 3010 includes a network of pipes with joints and crossings that fluidly interconnect different branches of conduit 3010. Alternatively, conduit 3010 can include a single pipe 3010 that meanders to different areas within space 1020a. According to various embodiments, conduit 3010 comprises a thin-walled conduit having an outer diameter of less than 2 inches, 1.5 inches, and / or 1 inch, and / or an inner diameter of less than 2 inches, 1.5 inches, and / or 1 inch. According to various embodiments, conduit 3010 comprises a material with a high thermal transfer coefficient (such as copper). Conduit 3010 is preferably rigid enough to maintain a relatively constant volume within conduit 3010 such that pressure changes within conduit 3010 are not significantly caused by changes in the internal volume within conduit 3010. According to various embodiments, the conduit includes (a) a conduit 3010 with a length of at least 5 linear feet, 10 linear feet, 15 linear feet, 20 linear feet, 30 linear feet, 40 linear feet, 50 linear feet, 60 linear feet, 70 linear feet, 80 linear feet, 90 linear feet, and / or 100 linear feet, (b) a conduit 3010 with a length less than 10,000 linear feet, 5,000 linear feet, 1,000 linear feet, 500 linear feet, and / or 100 linear feet, and / or (c) a conduit 3010 with a combined length between any two such values ​​(e.g., a conduit from 5 linear feet to 10,000 linear feet).

[0210] The fluid 3030 within pipe 3010 includes the following fluid: a fluid whose volume is highly temperature-dependent at the temperature of holding space 1020a and at the nominal pressure within pipe 3010 during normal operation of vehicle 1000.

[0211] Conduit 3010 is fluidly connected to pressure sensor 3020, which senses the pressure of fluid 3030 within conduit 3010. The pressure of fluid 3030 within sealed conduit 3010 varies with temperature; therefore, the pressure sensed by sensor 3020 indirectly measures the temperature within space 1020a. According to various embodiments, sensor 3020 includes a proportional pressure sensor. According to various embodiments, sensor 3020 is operatively connected to and controls pressure relief valve 1650 to open valve 1650 in response to sensor 3020 sensing that the pressure (and therefore temperature) within space 1020a exceeds a predetermined value (e.g., a value indicating a fire within space 1020a), and to release gas from tank 1030 to the surrounding environment 1120 (or another suitable location) via pressure relief valve 1650.

[0212] Instead of a proportional pressure sensor, sensor 3020 may include a rupture disc that, upon rupture, increases the pressure within a signal tube operatively connected to the pressure sensor of valve 1650.

[0213] Fluid 3030 is preferably pressurized relative to the pressure in space 1020a, so that sensor 3020 can detect a leak in pipe 3010 (i.e., if the sensed pressure in pipe 3010 drops toward or to the pressure in space 1020a).

[0214] According to various embodiments, the pressure sensor 3020 is disposed within the storage space 1020a or outside the storage space.

[0215] Double-wall safety hose

[0216] like Figures 9 to 10 As shown, the flexible double-walled safety hose 4000 can be used to safely deliver compressed hazardous gases (e.g., cryogenic compressed hydrogen, CNG, etc.). The double-walled hose 4000 includes an inner high-pressure hose 4010 disposed within an outer low-pressure hose 4020. The inner hose 4010 defines an internal space 4010a for delivering pressurized fluid via the safety hose 4000. The outer space 4020a is defined between the outer wall of the inner hose 4010 and the inner wall of the outer hose 4020.

[0217] The inner hose 4010 and the outer hose 4020 may be intermittently interconnected along their axial length by one or more spacers 4030 (e.g., struts), which tend to keep the hoses 4010 and 4020 axially concentric and / or longitudinally aligned. According to various embodiments, the spacers(s) 4030 may be flexible (e.g., ropes, elastomers) or rigid (e.g., metal rods). The spacers(s) 4030 may function under tension (e.g., like spokes of a bicycle wheel) and / or compression.

[0218] According to various embodiments, spacers 4030 include axial spacer rings. An inner hose passes through a central hole in the ring. The outer diameter of the ring is small enough to fit inside an outer hose 4020. The ring may be fluid-permeable and / or have longitudinal holes, allowing fluid in space 4020a to move through / through the ring, thereby preventing pressure build-up between adjacent rings. Alternatively, the inner and / or outer diameters of the ring may be selected such that fluid within space 4020a can pass between the inner hose 4010 and the ring and / or between the outer hose 4020 and the ring. According to various embodiments, the spacer ring may be an integral structure with an annular shape (e.g., like a donut or washer). Alternatively, the spacer ring may include multiple structures connected end-to-end around the circumference of the spacer ring to form an annular shape (e.g., like a beaded bracelet). The ring may include any suitable material (e.g., foam, elastomer, plastic, etc.). The ring can provide thermal insulation to better insulate the internal space 4010a from the surrounding environment 1120.

[0219] According to various embodiments, spacers 4030 are attached to the outside of the inner hose 4010 and / or the inside of the outer hose 4020 at spaced intervals. Alternatively, the axially spaced spacers 4030 may be connected to each other (e.g., by further spacers in the form of stretch lines) to help maintain axial spacing between the plurality of spacers 4030 along the axial length of the hose 4000.

[0220] However, the spacer 4030 may be omitted entirely without departing from the scope of one or more embodiments.

[0221] The double-walled hose 4000 includes a connector 4040 located at the axial ends of the hoses 4010 and 4020. According to various embodiments, the connector 4040 may be configured to fluidly connect the end of the internal space 4010a of the high-pressure hose 4010 to an additional high-pressure passage (e.g., any of the passages 350, 1560, and 1570 discussed above).

[0222] Connector 4040 can also be configured to fluidly connect an external space 4020a inside an external hose 4020 to another similar low-pressure external space within the connected external hose. Alternatively, connector 4040 can fluidly seal the ends of the external hose 4020 and the external space 4020a such that connector 4040 does not fluidly connect the external space 4020a to another low-pressure external hose 4020.

[0223] Connector 4040 can be any suitable type of connector for temporarily or permanently fluidly connecting the internal space 4010a of hose 4010 (or the external space 4020a of hose 4020) to other fluid channels(s). According to various embodiments, connector 4040 may include threaded connectors, bayonet connectors, quick-disconnect connectors, etc. Connector 4040 may alternatively be a permanent connector (e.g., a solder joint). According to various embodiments, connector 4040 includes valve 4110, which is fluidly connected to the ends of the internal space 4010a of hose 4010, respectively. Valve 4110 can be closed before connector 4040 is disconnected to prevent gas within the internal space 4010a from leaking into the environment 1120 when connector 4040 is disconnected. Conversely, after connector 4040 is connected to the supply and destination channels, valve 4110 can be opened to allow fluid to be delivered through the internal space 4010a of hose 4010.

[0224] According to various embodiments, valve 4110 may be operatively connected to connector 4040 mechanism to automatically open in response to connector 4040 being connected to another channel and to automatically close in response to connector 4040 being disconnected from another channel.

[0225] The hose 4000 also includes a ventilation hose 4050 having a first end 4050a and a second end 4050b. The first end 4050a is fluidly connected to the external space 4020a of the external hose 4020, and the second end 4050b leads to an area for the safe discharge of combustible gases (e.g., a portion of an environment 1120 separated from people and / or flames). As a result, the interior of the hose 4050 near end 4050a is in fluid communication with a portion of the external space 4020a and / or defines a portion of the external space 4020a.

[0226] A pressure relief valve 4060 is disposed in hose 4050. The normally closed pressure relief valve 4060 is configured to release pressure when the sensed pressure within the external space 4020a exceeds a predetermined pressure (e.g., (a) at least 145 psig, 200 psig, 300 psig, 400 psig, 500 psig, 750 psig, 1000 psig, 1500 psig, 2000 psig, 2500 psig, 3000 psig, 3500 psig, 4000 psig, 5000 psig, 6000 psig, and / or 7250 psig, (b) less than 7500 psig, 7250 psig, 7000 psig, 6000 psig, or 5000 psig). The fluid is opened and discharged from the external space 4020a through end 4050b at pressures between any two such values ​​(e.g., between 145 psig and 7500 psig, between 1000 psig and 5000 psig), and / or at pressures between any two such values ​​(e.g., between 145 psig and 7500 psig, between 1000 psig and 5000 psig). According to various embodiments, valve 4060 may include a self-actuated, pressure-sensitive valve that opens when the sensed pressure in the external space 4020a exceeds a predetermined pressure and closes when the sensed pressure in the external space 4020a drops below the predetermined pressure. Alternatively, valve 4060 may include a single-use normally closed valve, such as a rupture disc, which is calibrated to rupture / open at a predetermined pressure and remain open until replaced with a new / replacement valve 4060.

[0227] According to various embodiments, valve 4060 includes a visual and / or audible alarm that is triggered by the opening of valve 4060 to indicate to the operator of hose 4000 that valve 4060 is open and fluid is being discharged from end 4050b.

[0228] According to various embodiments, valve 4060 may additionally and / or alternatively be operably connected to valve 4110 at connector 4040. In such embodiments, opening of valve 4060 due to a sensed leak in hose 4010 causes valve 4110 in connector 4040 or near connector 4040 to close, thereby stopping further transmission of combustible gas to and from the end of hose 4010.

[0229] According to an embodiment where a portion of the hose 4020 is located in a safely ventilated area, the hose 4050 can be omitted, and at a location where hazardous gases are safely discharged, the valve 4060 is operatively connected directly to the external space 4020a within the hose 4020.

[0230] The hose 4000 includes a fluid supply channel 4070 that operatively connects a fluid source 4080 to an external space 4020a. As shown, the channel 4070 is connected to the external space 4020a via an intermediate hose 4050. However, the channel 4070 may alternatively be directly connected to the external space 4020a within the hose 4020. According to various embodiments, the source 4080 may include an ambient environment 1120 such that the fluid in the external space 4020a is air. Alternatively, the source 4080 may include an inert gas (such as nitrogen). According to various embodiments, the source 4080 is pressurized and connected to the channel 4070 via a pressure regulating valve that opens when the pressure within the external space 4020a is lower than a set pressure in the space 4020a, allowing fluid from the source 4080 to flow into the external space 4020a. According to various embodiments, the set pressure of the external space 4020a is (a) at least 50 psig, 75 psig, 100 psig, 150 psig, 200 psig, 250 psig, 300 psig, 400 psig, 500 psig, 750 psig, 1000 psig, 1250 psig, 1500 psig, 2000 psig, 2500 psig, 3000 psig, 3500 psig, and / or 4000 psig, (b) less than 5000 psig and 4500 psig. The pressures are 1g, 4000 psig, 3500 psig, 3000 psig, 2500 psig, 2000 psig, 1500 psig, 1250 psig, 1000 psig, 750 psig, 500 psig, 400 psig, 300 psig, 250 psig, 150 psig, and / or 100 psig, (c) and / or between any two such values ​​(e.g., between 50 psig and 5000 psig, between 2500 psig and 4000 psig). According to various embodiments, a pressure is set below a predetermined release pressure of valve 4060 (e.g., at least 25 psig, 50 psig, 75 psig, 100 psig, 150 psig, 200 psig, 250 psig, 300 psig, 400 psig, 500 psig, 750 psig, 1000 psig, 1100 psig, 1200 psig, 1300 psig, 1400 psig, and / or 1500 psig lower than the predetermined release pressure) such that fluid flow from source 4080 to hose 4020 will not cause valve 4060 to open.

[0231] like Figure 10As shown, according to one or more embodiments (e.g., embodiments where the pressure of the fluid in source 4080 is lower than a set pressure in external space 4020a), compressor 4090 is disposed along channel 4070. The inlet of compressor 4090 is fluidly connected to source 4080 (e.g., air from the surrounding environment) via channel 4070. The outlet of compressor 4090 is fluidly connected to external space 4020a via channel 4070 (or directly connected). Compressor 4090 is configured to compress fluid and deliver fluid from source 4080 to the internal space 4020a of hose 4020. According to various embodiments, compressor 4090 may be a pressure-regulating compressor that activates when the sensed pressure within external space 4020a (e.g., sensed by a pressure sensor in hose 4020) drops below a set pressure.

[0232] According to various embodiments, a check valve may be provided in channel 4070 to prevent fluid from flowing from external space 4020a to source 4080 via channel 4070. In the event of a leak in high-pressure hose 4010, the check valve preferably prevents high-pressure hazardous gas from flowing back to source 4080 through channel 4070.

[0233] According to various embodiments, the rated pressure of hose 4010 is (a) at least 2500 psig, 3000 psig, 3500 psig, 4000 psig, 4500 psig, 5000 psig, 6000 psig, 7000 psig, 8000 psig, 9000 psig, and / or 10000 psig, (b) less than 15000 psig, 12500 psig, 10000 psig, 9000 psig, 8000 psig, 7000 psig, 6000 psig, 5000 psig, 4500 psig, 4000 psig, 3500 psig, and / or 3000 psig, and / or (c) pressure between any two such values ​​(e.g., between 2500 psig and 15000 psig, between 3000 psig and 6000 psig).

[0234] According to various embodiments, the hose 4010 is rated for lower and / or cryogenic temperatures, such as the following temperatures: (a) less than or equal to 233K, 220K, 200K, 180K, 160K, 140K, 130K, 120K, 110K, 100K, 90K, and / or 80K, (b) at least 40K, 50K, 60K, 70K, 80K, 90K, 100K, 150K, and / or 200K, and / or (c) temperatures between any two such values ​​(e.g., between 40K and 223K, between 77K and 100K, between 77K and 90K). According to various embodiments, hose 4000 is well-suited for conveying very cold (e.g., cryogenic) fluids through the internal space 4010a of hose 4010 because the external hose 4020 and the fluid within the external space 4020a of the external hose 4020 provide thermal insulation between the internal hose 4010 and the surrounding environment 1120 outside the external hose 4020.

[0235] According to various embodiments, the pressurized portions of the external hose 4020 and the ventilation hose 4050 are rated pressures of (a) at least 500 psig, 750 psig, 1000 psig, 1250 psig, 1500 psig, 2000 psig, 2500 psig, 3000 psig, 3500 psig, 4000 psig, 5000 psig, 6000 psig, and / or 7000 psig, and (b) less than 8000 psig, 7000 psig, 6000 psig, and / or 7000 psig, respectively. 0 psig, 5000 psig, 4500 psig, 4000 psig, 3500 psig, 3000 psig, 2500 psig, 2000 psig, 1500 psig, 1250 psig, 1000 psig, 900 psig, 800 psig, 750 psig, 700 psig, and / or 650 psig, and / or (c) pressure between any two such values ​​(e.g., between 500 psig and 8000 psig).

[0236] According to various embodiments, the rated flow rate of the external space 4020a through the external hose 4020 (and in embodiments including a ventilation hose 4050) is higher than the rated flow rate of the internal hose 4010, such that the external hose 4020 and the external space 4020a can accommodate the entire gas flow through the internal space 4010a of the internal hose 4010 (e.g., if the hose 4010 is completely cut off, causing all the airflow through the hose 4010 to leak into the external space 4020a of the external hose 4020), without causing the external hose 4020 (and the ventilation hose 4050, if used) to burst. According to various embodiments, the predetermined release pressure of the valve 4060 is preferably lower than the rated pressure of the hose 4020 (and the hose 4050, if the hose 4050 is used), such that the valve 4060 opens before the hoses 4020 and 4050 burst.

[0237] According to various embodiments, source 4080, channel 4070, and compressor 4090 are omitted. In such embodiments, external space 4020a may be fluid-sealed and may be pressurized, unpressurized, or under a slight vacuum. If external space 4020a is unpressurized, it may be filled with gas (e.g., air or an inert gas such as nitrogen) and sealed, or it may be empty. In various embodiments, a leak of pressurized gas from internal space 4010a will leak into external space 4020a, thereby increasing the pressure within external space 4020a. This may trigger gas leak sensor 4100 and / or open pressure relief valve 4060, releasing flammable gas in a safe location.

[0238] According to various embodiments, if the external space 4020a is typically maintained under a slight vacuum pressure, the hose 4020 is structurally designed to withstand this vacuum pressure without leakage. This slight vacuum embodiment can rely on a fully scaled-down space 4020a that is sealed under a slight vacuum pressure. Alternatively, a compressor (e.g., similar to compressor 4090, but driving gas in the opposite direction) can be used to maintain a slight negative pressure within the external space 4020a relative to the surrounding environment. This slight vacuum pressure within space 4020a can help prevent or stop any gas leaking from hose 4010 into space 3020a from leaking into the surrounding environment. This vacuum pressure system is particularly useful in preventing small-volume leaks in hose 4010 from causing gas to leak into the surrounding environment around hose 4000.

[0239] According to one or more embodiments, one or more gas sensors 4100 are positioned to sense flammable / hazardous gases in the external space 4020a of the external hose 4020, and thereby detect leaks in the internal hose 4010. According to various embodiments, the sensors 4100 may be operatively connected to an alarm (e.g., a visual and / or audible alarm) such that if a flammable gas concentration above a certain level is detected in the external space 4020a of the hose 4020, the alarm alerts the hose operator.

[0240] According to one or more embodiments, the plurality of sensors 4100 are operatively connected to and control the valve 4060 to open the valve 4060 when a concentration of combustible gas above a certain level is detected in the external space 4020a. Alternatively, the plurality of sensors 4100 are not operatively connected to the valve 4060.

[0241] According to one or more embodiments, (a plurality of) sensors 4100 are operatively connected to and control valve 4110 to close valve 4110 when a combustible gas concentration above a certain level is detected in external space 4020a (e.g., due to a leak in hose 4010), thereby allowing fluid to be delivered to and from the end of hose 4010.

[0242] However, according to an alternative embodiment, the (multiple) sensors 4100 are completely omitted.

[0243] In the following text, see references Figure 10 The operation of hose 4000 is described below. Before using hose 4000 to deliver pressurized gas through hose 4010, the external space 4020a of external hose 4020 is pressurized to a set pressure. Before or after pressurizing external hose 4020, upstream connector 4040 is connected to a pressurized gas (e.g., hydrogen or natural gas) source to deliver pressurized gas through internal space 4010a of internal hose 4010. Downstream connector 4040 is connected to a destination channel for delivering pressurized gas through internal hose 4010. One or more valves in the source channel and / or destination channel (and / or valve 4110 of hose 4010) are opened to deliver pressurized gas from the source to the destination via internal space 4010a of hose 4010. If hose 4010 leaks, gas will leak into the external space 4020a of external hose 4020, causing the pressure in external space 4020a to rise. This will cause valve 4060 to open and release the combustible gas to a safe position at end 4050b of discharge hose 4050. The opening of valve 4060 may automatically trigger an alarm and / or close valve 4110.

[0244] Dual-pressure gas transfer hose system and method

[0245] like Figure 11 As shown, the dual-pressure gas transfer hose system 5000 can be used to transfer low-pressure and / or high-pressure compressed gases (e.g., cryogenic compressed hydrogen, CNG, etc.) to a destination (e.g., tank 1030, fuel cell 5005).

[0246] According to various embodiments involving loading tank 1030, the gas transfer can occur while maintaining high pressure within tank(s) 1030 (e.g., the gas transfer is combined with hydraulic, liquid nitrogen, and / or gaseous nitrogen ballast to maintain high pressure within tank 1030, as explained above). System 5000 includes a high-pressure channel 5010 and a low-pressure channel 5020.

[0247] The high-pressure channel 5010 has a first inlet 5010a and a first outlet 5010b. The high-pressure channel 5010 has the following rated pressures: (a) at least 3000 psig, 4000 psig, 5000 psig, 6000 psig, 7000 psig, 8000 psig, 9000 psig, 10000 psig, 11000 psig, 12000 psig, 13000 psig, 14000 psig, and / or 15000 psig, (b) less than 18000 psig, 17000 psig, 16000 psig, 15000 psig. 14000 psig, 13000 psig, 12000 psig, 11000 psig, 10000 psig, 9000 psig, 8000 psig, 7500 psig, 7000 psig, 6500 psig, 6000 psig, 5500 psig, and / or 5000 psig, and / or (c) pressures between any two such values ​​(e.g., between 3000 psig and 18000 psig, between 3000 psig and 6000 psig). According to various embodiments, the high-pressure channel 5010 has an inner diameter of less than 5 inches, 4 inches, 3 inches, 2 inches, and / or 1 inch. Inlet 5010a is configured to connect to a high-pressure gas source 5015 (e.g., a gas with the following pressures: (a) at least 2500 psig, 3000 psig, 4000 psig, 5000 psig, 6000 psig, 7000 psig, 8000 psig, 9000 psig, 10000 psig, 11000 psig, 12000 psig, 13000 psig, 14000 psig, and / or 15000 psig, (b) less than 20000 psig). 1g, 15000psig, 14000psig, 13000psig, 12000psig, 11000psig, 10000psig, 9000psig, 8000psig, 7500psig, 7000psig, 6500psig, 6000psig, 5500psig, and / or 5000psig, and / or (c) pressure between any two such values ​​(e.g., between 3000psig and 20000psig)).

[0248] Pressure regulating valve 5035 may optionally be disposed in channel 5010, and if the upstream pressure in channel 5010 (e.g., on the inlet 5010a side of valve 5035) exceeds the downstream pressure in channel 5010 (e.g., on the outlet 5010b side of valve 5035), pressure regulating valve 5035 is set to open. Therefore, valve 5035 prevents gas from flowing back to inlet 5010a through valve 5035. According to various embodiments, valve 5035 may be replaced by a check valve to provide the same function.

[0249] The low-pressure channel 5020 has an inlet 5020a and an outlet 5020b. The low-pressure channel 5020 has a rated pressure lower than that of the first channel. According to various embodiments, the rated pressure of channel 5020 is at least 500 psig, 600 psig, 700 psig, 800 psig, 900 psig, 1000 psig, 2000 psig, 3000 psig, 4000 psig, 5000 psig, 6000 psig, and / or 7000 psig lower than that of the high-pressure channel 5010. According to various embodiments, the rated pressure of the low-pressure channel 5020 is (a) at least 500 psig, 600 psig, 700 psig, 800 psig, 900 psig, 1000 psig, 2000 psig, 3000 psig, 4000 psig, 5000 psig, 6000 psig, and / or 7000 psig, (b) less than 8000 psig, 7000 psig, 6000 psig, 5000 psig, 4000 psig, 3000 psig, 2500 psig, 2000 psig, 1500 psig, 1000 psig, and / or 750 psig, and / or (c) a pressure between any two such values ​​(e.g., between 500 psig and 8000 psig). According to various non-limiting embodiments, the second channel 5020 has an inner diameter of at least 2 inches, 3 inches, 4 inches, 5 inches, and / or 6 inches. Inlet 5010a is configured to connect to a low-pressure gas source 5025 (e.g., a gas at the following pressures: (a) at least 250 psig, 300 psig, 400 psig, 500 psig, 600 psig, 700 psig, 800 psig, 900 psig, 1000 psig, 2000 psig, 3000 psig, 4000 psig, 5000 psig, 6000 psig, and / or 7000 psig, (b) less than 8000 psig, 7000 psig, 6000 psig, 5000 psig, 4000 psig, 3000 psig, 2000 psig, and / or 1500 psig, and / or (c) a pressure between any two such values ​​(e.g., between 250 psig and 8000 psig)).

[0250] Outlet 5020b is connected to channel 5010 via check valve 5030, pressure regulating valve 5040, and / or second check valve 5050, which may be arranged in series between outlet 5020b and channel 5010. Check valves 5030 and 5050 prevent fluid from flowing from high-pressure channel 5010 to low-pressure channel 5020, which helps ensure that the pressure in low-pressure channel 5020 is maintained within the rated pressure of channel 5020. Pressure regulating valve 5040 is configured to close when the pressure in high-pressure channel 5010 exceeds a predetermined pressure (e.g., the rated pressure of low-pressure channel 5020). According to various embodiments, any one or both of check valves 5030 and 5050 may be omitted, and valve 5040 is used to prevent high-pressure gas from flowing back into low-pressure channel 5020. According to various embodiments, the pressure regulating valve 5040 may be omitted, and one or two check valves 5030, 5050 are used to prevent gas from flowing back into the channel 5020.

[0251] The third passage 5070 extends from the low-pressure passage 5020 to the high-pressure passage 5010 via a check valve 5080 (or pressure regulating valve), a compressor 5090, and a check valve 5100 (or pressure regulating valve). As the third passage 5070 advances from the low-pressure passage 5020 to the high-pressure passage 5010, the check valve 5080, compressor 5090, and check valve 5100 are sequentially arranged within the third passage 5070. The check valves 5080 and 5100 each prevent fluid from flowing through passage 5070 from the high-pressure passage 5010 to the low-pressure passage 5020. The compressor 5080 is configured to compress the gas received from the low-pressure passage 5020 and deliver the resulting compressed gas to the high-pressure passage 5010. The portion of channel 5070 upstream of compressor 5080 may have a lower rated pressure (e.g., the same rated pressure as channel 5020), and the portion of channel 5070 downstream of compressor 5080 may have a relatively higher rated pressure (e.g., the same rated pressure as channel 5010).

[0252] According to one or more embodiments, an optional ventilation passage 5200 extends from the low-pressure passage 5020 (directly or via a third passage 5070). A valve 5210 is disposed in the ventilation passage 5020 to allow or prevent gas from being discharged from the passage 5020 via the ventilation passage 5200. A catalytic heater 5220 or other combustion mechanism is disposed at the end of the ventilation passage 5200 to purge / combust the gas discharged into the ambient environment 1120 via the passage 5200.

[0253] Inlets 5010a, 5020a and outlets 5010b, 5020b may include connectors 5230 (e.g., threaded connectors, quick-disconnect connectors, bayonet connectors) for connecting channels to upstream gas sources 5015, 5025 and / or downstream gas destinations (e.g., channel 1560, which leads to one or more tanks 1030 and / or other destinations or users of the high-pressure gas (e.g., fuel cell 5005)).

[0254] According to one or more embodiments, channels 5010, 5020 include one or more flexible hoses 5010, 5020 extending from inlets 5010a, 5020a, and connectors 5230 at outlets 5010b, 5020b. Using such flexible hoses 5010, 5020 makes it easier to connect the hose inlet connectors 5230 to gas sources 5015, 5025, respectively. However, according to alternative embodiments, channels 5010, 5020 are rigid channels (e.g., rigid pipes). Even if the pressure in channel 5010 exceeds the rated pressure of channel 5020, system 5000 ensures that the pressure in channel 5020 does not exceed the rated pressure of channel 5020.

[0255] According to various embodiments, one or both of the channels 5010, 5020 (or any other channel discussed herein) may include a double-walled hose, such as the hose 4000 discussed above.

[0256] refer to Figure 11 The operation of the dual-pressure hose system 5000 is described below. When the system 5000 is used to deliver gas from a high-pressure gas source 5015, the high-pressure gas source 5015 is connected to an inlet 5010a in a high-pressure channel 5010. An outlet 5010b is connected to a destination (e.g., tank 1030 and / or fuel cell 5005). The gas is then transported to its destination via channel 5010.

[0257] While or alternatively, gas can be loaded from a low-pressure source 5025 via a channel 5020, gas can be loaded from a high-pressure source 5015 via an inlet 5010a. For this purpose, inlet 5020a is connected to the low-pressure gas source 5025, and outlet 5010b is connected to a channel 1560 leading to a destination (e.g., tank 1030 and / or fuel cell 5005). If the pressure at the destination (and therefore the portion of high-pressure channel 5010 between valve 5035 and the destination) is lower than the pressure at the low-pressure gas source 5025, valve 5040 will open, and gas will be delivered from the low-pressure source 5025 to the destinations via channels 5020 and 5010.

[0258] However, if the pressure at the destination exceeds the pressure of the low-pressure source 5025, the gas will not naturally flow from the low-pressure source 5025 through check valves 5030 and 5040 to the higher-pressure destination. In this case, compressor 5080 can be used to compress the gas from the low-pressure source 5025 to deliver the gas from the low-pressure source 5025 to the destination via channel 5020, channel 5070, channel 5010, and channel 1560. A refrigeration system can be added to any of channels 5070, 5010, and 5020 to cool the gas passed through them (e.g., consider the temperature rise caused by compression by compressor 5080).

[0259] If excess gas is supplied by a low-pressure source 5025 (e.g., a wellhead that produces unwanted or excess natural gas), valve 5210 can be opened and the excess gas is burned via catalytic heater 5220.

[0260] The dual-pressure hose system 5000 discussed above is configured to load (multiple) tanks 1030 or to supply compressed gas to a destination 5005. However, according to various alternative embodiments, such as... Figure 12 As shown, the dual-pressure hose system 6000 is additionally and / or alternatively configured to unload compressed gas from tank(s) 1030 and / or location 5005. Except as explained below, system 6000 is generally similar to system 5000. Figure 12 As shown, valves 5030, 5040, and 5050 of system 5000 are replaced with valve 6010, buffer tank 6020, and valve 6030, which are sequentially arranged along a channel extending between low-pressure channel 5020 (e.g., connector 5230) and high-pressure channel 5010, and work together to ensure that high-pressure gas from hose 5010 never overpressures low-pressure hose 5020. Figure 12As shown, valve 6010 is a pressure regulating valve that senses the pressure in low-pressure hose 5020 to automatically close valve 6010 when the sensed pressure in low-pressure hose 5020 exceeds a predetermined value (e.g., 60%, 70%, 80%, 90%, and / or 100% of the rated pressure of low-pressure hose 5020), and automatically opens valve 6010 when the sensed pressure in low-pressure hose 5020 drops below a predetermined value (e.g., the same value used to close valve 6010, or a lower value (e.g., 50%, 60%, 70%, 80%, 90%, and / or 95% of the rated pressure of low-pressure hose 5020)). When valve 6010 is closed, buffer tank 6020 accumulates compressed gas to prevent over-pressurization of the passage between valves 6010 and 6030 should valve 6010 close abruptly. Valve 6030 is a pressure regulating valve configured to open when the pressure in a passage (connecting valves 6010 and 6030) drops below a predetermined pressure (e.g., 60%, 70%, 80%, 90%, and / or 100% of the rated pressure of low-pressure hose 5020) and to close when the pressure in a passage (between valves 6010 and 6030) rises above a predetermined pressure (e.g., the same value used to close valve 6030, or a lower value (e.g., 50%, 60%, 70%, 80%, 90%, and / or 95% of the rated pressure of low-pressure hose 5020)).

[0261] In the following text, see references Figure 12 The operation of the dual-pressure hose system 6000 is described below. The operation of loading system 6000 with tank(s) 1030 or destination 5005 is generally similar to the loading process of system 5000, as explained above. However, system 6000 can also be used to unload compressed gas to a low-pressure destination (which replaces or is the same as source 5025), which is connected to low-pressure hose 5020 via connector 5230. The operator opens valve 6010, which allows higher-pressure gas from tank 1030, destination 5005, and / or high-pressure gas source 5015 to flow sequentially from high-pressure hose 5010 through valve 6030, valve 6010, outlet 5020b, low-pressure hose 5020, and inlet 5020a to the low-pressure gas destination. When unloading is complete, the operator closes valve 6010 (which increases the pressure in buffer 6020) and valve 6030, while relying on buffer tank 6020 to prevent overpressure when valve 6010 is closed but before valve 6030 is fully closed.

[0262] Systems using cryogenic compressed hydrogen at oxygen-consuming equipment

[0263] Figure 15System 7500 is shown, in which cryogenic compressed hydrogen is used at oxygen-consuming equipment 7510 (e.g., a steel plant, other equipment with oxygen-consuming processes). Channel 7520 extends from a source of cryogenic compressed hydrogen 7530 (e.g., ship 1000, railcar, barge, system 100, system 7000, etc.) through heat exchanger 7540, through expander 7550, and to equipment 7510. System 7500 also includes a refrigeration system 7600 for extracting heat from air separation unit 7610.

[0264] like Figure 15 As shown, cryogenic compressed hydrogen arrives from source 7530 (e.g., at a temperature of about -320℉), leaves heat exchanger 7540 at a temperature of about 100℉, leaves expander at a pressure of less than 10 bar, and is delivered to device 7510 for use.

[0265] The refrigeration system 7600 includes a coolant circuit / channel 7620 through which coolant (e.g., nitrogen) circulates between heat exchangers 7540 and 7630 of the ASU 7610. According to various embodiments, heat exchanger 7540 uses cryogenic compressed hydrogen in channel 7520 to cool the coolant in circuit 7620 to a temperature of approximately -310℉. According to various embodiments, heat exchanger 7630 then uses the cooled coolant in circuit 7620 to absorb heat from the ASU 7610, causing the coolant to exit heat exchanger 7630 at a temperature of approximately 90℉. A pump or compressor may be provided in circuit 7620 to drive the circulation of the coolant.

[0266] According to an alternative embodiment, excess nitrogen generated by ASU 7610 is released into the atmosphere or supplied from ASU 7610 to source 7530 via a channel (e.g., to supplement the nitrogen supply of source 7530). For example, in an embodiment where source 7530 is the aforementioned vessel 1000, nitrogen from ASU 7610 can be used to supplement the nitrogen supply of vessel 1000 (e.g., by replenishing liquid nitrogen container 1510).

[0267] ASU 7610 generates gaseous oxygen (O2) 7640, which flows from ASU 7610 to device 7510 via channel 7650 and is subsequently used by device 7510.

[0268] like Figure 15As shown, the energy generated by the turboexpander 7550 is recovered and transferred to the ASU 7610, where it is used to power the ASU 7610. For example, a generator attached to the output shaft of the turboexpander can generate electricity, which is then transferred to the ASU 7610 via the electrical conduit 7660 and used by the ASU 7610.

[0269] Alternatively, the output shaft of the turboexpander 7550 may be mechanically coupled to the input shaft of the ASU 7610 to mechanically drive (directly or via a gearbox or transmission) one or more components of the ASU 7610 (e.g., a compressor or pump).

[0270] System 7500 thus utilizes the low temperature and high compression of cryogenically compressed hydrogen to effectively cool and / or power ASU 7610, while simultaneously supplying hydrogen to device 7510 at a temperature (higher) more useful to device 7510 than the cryogenic compression temperature of hydrogen supplied by source 7530, and / or at a pressure (lower) more useful to device 7510 than the pressure of hydrogen supplied by source 7530. Similarly, expander 7550 operates most efficiently at a higher inlet temperature (where the gas entering at both high temperature and high pressure has more energy) to supply more energy to ASU 7610 (e.g., via conduit 7660).

[0271] System for generating cryogenic compressed hydrogen

[0272] Figure 16 A system 8000 for generating cryogenic compressed hydrogen is shown. System 8000 includes a hydrogen source 8010 that supplies hydrogen via channel 8020 to a hydrogen-consuming device 8030 (e.g., a steel furnace, device 7510), which can use hydrogen as an oxide reducing agent. Excess hydrogen flows from source 8010 via channel 8050 to a cryogenic compressed hydrogen generator 8040. Generator 8040 then delivers the cryogenic compressed hydrogen to destination 8060 via channel 8070. An air separation unit 8080 (which may be air separation unit 7610 discussed above) separates air into gaseous oxygen and liquid nitrogen (and smaller amounts of other gases in the air). Air separation unit 8080 then supplies the separated gaseous oxygen to the steel furnace via channel 8090. Air separation unit 8080 supplies the separated nitrogen (e.g., liquid nitrogen) to generator 8040 via channel 8100. The generator 8040 combines its cryogenic compression of hydrogen with nitrogen pretreatment and / or cooling.

[0273] The hydrogen source 8010 may include a hydrogen generator 8010. The hydrogen generator 8010 may produce hydrogen via hydrolysis using electricity, and / or by any other method for producing hydrogen.

[0274] Destination 8060 may include a cryogenic compressed hydrogen tank (e.g., tank 1030) which may be installed on a ship (e.g., ship 1120), a railcar, or other vehicle.

[0275] Unless otherwise specified herein, all pressures described are gauge pressures, not absolute pressures.

[0276] The foregoing illustrated embodiments are provided to illustrate the structural and functional principles of various embodiments, and the illustrated embodiments are not intended to be limiting. Rather, the principles of the invention are intended to cover any and all changes, alterations, and / or substitutions (e.g., any changes within the spirit and scope of the appended claims).

Claims

1. A method for cooling compressed gas, the method comprising: The first stream of compressed gas is split into a second and a third stream; The third flow expands and cools; as well as Downstream of the third stream, which is expanded and cooled, the third stream and the second stream are passed through a heat exchanger that transfers heat from the second stream to the third stream.

2. The method as described in claim 1, wherein, The heat exchanger includes a first heat exchanger, and The method further includes: passing the third stream and the first stream downstream of the first heat exchanger through a second heat exchanger, the second heat exchanger transferring heat from the first stream to the third stream.

3. The method of claim 2, further comprising actively cooling the first stream after the first stream leaves the second heat exchanger.

4. The method of claim 1, wherein, The expansion cooling includes JT cooling.

5. The method of claim 1, wherein, The expansion cooling includes passing the third flow through the turbine expander.

6. The method of claim 1, further comprising controlling the flow rate of the second stream relative to the third stream to ensure that the temperature of the second stream is within a predetermined temperature range when it exits the heat exchanger.

7. The method of claim 1, further comprising: The third stream is compressed downstream of the heat exchanger to form a fourth stream; as well as The fourth and fifth streams are merged to form the first stream.

8. A system for cooling compressed gas, the system comprising: A compressed gas inlet, which is used to receive compressed gas; Heat exchanger; Shunt; Expansion cooler; Compressed gas outlet; A first channel extends from the inlet to the splitter; The second channel extends sequentially from the splitter through the heat exchanger and to the compressed gas outlet; as well as The third channel extends sequentially from the splitter through the expansion cooler and through the heat exchanger.

9. The system of claim 8 further includes a cooling unit disposed in the first channel.

10. The system of claim 8, wherein: The heat exchanger includes a first heat exchanger; The system also includes a second heat exchanger; The first channel passes through the second heat exchanger; and The third channel sequentially flows from the splitter through the expansion cooler, through the first heat exchanger, and then through the second heat exchanger.

11. An assembly for transporting cryogenic compressed hydrogen, the assembly comprising: vehicle; An insulated space supported by the vehicle; A glass-reinforced storage tank disposed within the insulating space, the storage tank defining an internal space; as well as Cryogenic compressed hydrogen stored in the tank; The pressure inside the tank is between 900 psig and 10000 psig, and the temperature inside the tank is between 60 K and 210 K.

12. The assembly as claimed in claim 11, wherein, The density of the cryogenic compressed hydrogen in the tank is at least 2.0 lbm / ft. 3 .

13. The assembly as claimed in claim 12, wherein, The cryogenic compressed hydrogen occupies at least 75% of the volume of the tank.

14. The assembly as claimed in claim 11, wherein, The vehicles mentioned include ships.

15. The assembly of claim 11, further comprising a pressure relief valve operably connected to the tank, and the pressure relief valve being configured to: release gas from the tank to the surrounding environment outside the vehicle if the pressure exceeds a predetermined pressure.

16. The assembly as claimed in claim 15, wherein, The pressure relief valve includes an emergency rupture disc.

17. The assembly of claim 11, further comprising a pressure relief valve operably connected to the insulating space, and configured to release gas from the insulating space to the surrounding environment outside the vehicle if the pressure within the insulating space exceeds a predetermined pressure.

18. The assembly as claimed in claim 17, wherein, The predetermined pressure relative to the ambient pressure is between 0.1 psi and 3.0 psi.

19. The assembly as claimed in claim 15, wherein, The pressure relief valve includes an emergency blast hatch.

20. The assembly as claimed in claim 11, wherein, The tank contains composite reinforcing materials.

21. The assembly as claimed in claim 11, wherein, The can contains glass that is stronger at the stated temperature than at 273K.

22. The assembly as claimed in claim 11, wherein, The tank includes a lined storage cylinder, wherein the lining comprises HDPE, PA-6, or 316L stainless steel.

23. The assembly of claim 11, further comprising an overflow valve operably connected to the tank.

24. The assembly as claimed in claim 11, wherein, The vehicle in question is a ship.

25. An assembly for transporting cryogenic compressed hydrogen, the assembly comprising: vehicle; An insulated space supported by the vehicle; Liquid nitrogen is placed in the insulating space; A storage tank disposed within the insulating space, the storage tank defining an internal space; as well as Cryogenic compressed hydrogen stored in the tank; The pressure inside the tank is between 900 psig and 10000 psig, and the temperature inside the tank is between 60 K and 210 K.

26. The assembly as claimed in claim 25, wherein, The liquid nitrogen, which is disposed in the insulating space, is disposed on the outside of the tank.

27. The assembly of claim 26, further comprising: A nitrogen liquefaction system, the nitrogen liquefaction system being supported by the vehicle and the nitrogen liquefaction system being configured to liquefy gaseous nitrogen; A liquid nitrogen channel that operatively connects the liquefaction system to the insulating space and is configured to transfer liquid nitrogen from the liquefaction system to the insulating space; as well as A nitrogen return channel operatively connects the insulating space to the liquefaction system and is configured to transfer gaseous nitrogen from the insulating space to the liquefaction system, such that the liquefaction system can liquefy gaseous nitrogen received from the insulating space via the nitrogen return channel.

28. The assembly as claimed in claim 27, wherein, The liquefaction system is configured to maintain the pressure within the insulated space at 0.1 psig to 2.0 psig relative to the ambient pressure outside the vehicle.

29. The assembly as claimed in claim 26, wherein, The insulating space includes a recess that is shaped and configured to collect and retain liquid nitrogen.

30. The assembly of claim 27, further comprising a nitrogen generator configured to collect nitrogen and isolate nitrogen from ambient air, and to provide isolated nitrogen to the insulated space, wherein, The isolated nitrogen is at least 90% nitrogen.

31. The assembly as claimed in claim 30, wherein, The nitrogen generator includes a compressor and a pressure swing absorption device, the compressor being configured to compress ambient air and the pressure swing absorption device being configured to separate nitrogen from the compressed air.

32. The assembly as claimed in claim 25, wherein, The storage tank includes a glass-reinforced storage tank.

33. The assembly as claimed in claim 25, wherein, The liquid nitrogen, which is disposed in the insulating space, is disposed in the internal space.

34. The assembly as claimed in claim 33, wherein, The tank includes a gas port and a liquid port, the gas port being fluidly connected to the upper portion of the internal space and the liquid port being fluidly connected to the lower portion of the internal space.

35. The assembly of claim 33 further includes a baffle disposed within the tank.

36. The assembly of claim 33, further comprising a float in the interior space, the float being vertically movable within the interior space, the float dividing the interior space into an upper portion above the float and a lower portion below the float, the float having a density higher than that of the cryogenic compressed hydrogen and lower than that of the liquid nitrogen.

37. The assembly of claim 25, further comprising: Liquid nitrogen storage container; A liquid nitrogen supply channel that connects the container to the tank; as well as A pump, which is positioned and configured to pump liquid nitrogen from the container into the interior space.

38. The assembly as claimed in claim 37, wherein, The pump is configured to pump liquid nitrogen into the interior space during the unloading of the cryogenic compressed hydrogen from the tank, so as to displace the cryogenic compressed hydrogen in the interior space and facilitate the unloading of the cryogenic compressed hydrogen from the tank substantially isothermally and isobarically.

39. The assembly of claim 37, further comprising: A liquid nitrogen return channel connects the liquid nitrogen storage container to the internal space; and A valve is disposed in the liquid nitrogen return channel. The valve has an open state in which liquid nitrogen can flow from the internal space to the container, and a closed state to prevent liquid nitrogen from flowing from the internal space to the container.

40. The assembly as claimed in claim 39, wherein, The valve includes a pressure regulating valve configured to open when the pressure in the tank exceeds a predetermined pressure.

41. The assembly as claimed in claim 40, wherein, The valve is configured to facilitate substantially isobaric loading of the tank with cryogenic compressed hydrogen.

42. A method of transporting cryogenic compressed hydrogen using a vehicle, said vehicle having an insulated space and a storage tank disposed within said insulated space, said storage tank defining an internal space, said method comprising: Cool the temperature within the internal space to between 77K and 90K; The internal space is pressurized to a pressure between 900 psig and 10000 psig; and When the temperature is between 60K and 210K and the pressure is between 900psig and 10000psig, cryogenic compressed hydrogen is delivered into the internal space.

43. The method of claim 42, wherein, The cooling occurs when the pressure within the internal space is less than 300 psig.

44. The method of claim 42, wherein, The cooling process involves placing liquid nitrogen in the insulated space outside the tank when the pressure inside the internal space is less than 300 psig.

45. A method for manufacturing a storage tank for storing compressed fluid, the method comprising: Insert the expandable support through the hole into the liner; The support extends radially within the internal space inside the liner to mechanically support the liner; When the support is disposed within the liner, a composite reinforcement is wound around the liner, wherein the composite reinforcement comprises glass and resin; Curing of the resin; To retract the support; and The mechanical support is removed from the liner via the holes in the liner.

46. ​​The method of claim 45, wherein, The lining comprises HDPE, PA-6, or 316L stainless steel.

47. The method of claim 45, wherein, The composite reinforcement comprises at least 60% glass fiber and at least 10% resin.

48. The method of claim 47, wherein, The composite reinforcement contains at least 10% insulator.

49. The method of claim 48, wherein, The insulator contains perlite.

50. The method of claim 48, wherein, The composite reinforcement contains a flame retardant.

51. The method of claim 45, wherein, The lining has an expansion joint.

52. The method of claim 51, wherein, The expansion joint includes a corrugated portion in the lining that facilitates the expansion and contraction of the lining.

53. The method of claim 51, wherein, The tank includes a cylinder that is elongated in the axial direction, and wherein the expansion joint facilitates the expansion and contraction of the liner along the axial direction.

54. The method of claim 45, wherein, The tank includes a cylinder body that is elongated in the axial direction of the cylinder body, and wherein the winding occurs when the axial direction is within 10° of the vertical orientation.

55. The method of claim 45, wherein, The winding includes: The liner is wound using a first sublayer of glass-hardened material and a first sublayer of resin; Curing the first sublayer of the resin; and The second sublayer of the glass-curing material and the second sublayer of the resin are wound around the first sublayer of the glass-curing material and the first sublayer of the resin.

56. An assembly for transporting compressed combustible gas, the assembly comprising: vehicle; Storage space, which is supported by the vehicle; A gas storage tank disposed within the storage space and defining an internal space, the storage tank having a pressure relief valve configured to release gas from the internal space into the insulating storage space when the pressure within the internal space exceeds a predetermined pressure; Compressed gas, the compressed gas being stored in the internal space of the storage tank; A gas sensor is disposed within the storage space and configured to detect when the concentration of the gas in the storage space outside the storage tank exceeds a predetermined concentration; At least one fan is connected to the storage space and is configured to exchange air between the storage space and the surrounding environment around the vehicle. as well as A fan controller operatively connected to the gas sensor and the at least one fan, the fan controller being configured to increase the air exchange rate between the storage space and the surrounding environment in response to sensing that the gas in the storage holder outside the storage tank exceeds a predetermined concentration.

57. The assembly of claim 56 further comprises a plurality of additional gas storage tanks disposed within the storage space, each of the plurality of additional gas storage tanks having an internal space and a pressure relief valve configured to release gas from the corresponding gas storage tank into the storage space if the pressure in the internal space of the corresponding gas storage tank exceeds a predetermined pressure.

58. The assembly as claimed in claim 57, wherein, The internal space of each of the plurality of storage tanks is fluidly isolated from each other.

59. The assembly as claimed in claim 56, wherein, The at least one fan includes at least one intake fan and at least one exhaust fan, the at least one intake fan being positioned to blow ambient air from the surrounding environment into the insulating storage holder, and the at least one exhaust fan being positioned to blow air from the insulating storage holder to the surrounding environment.

60. An assembly for transporting compressed combustible gas, the assembly comprising: A container that defines a storage space; A compressed gas storage tank, wherein the compressed gas storage tank is disposed within the storage space; A pressure relief valve is connected to the tank so that pressurized gas stored in the tank can be released when the valve is opened; as well as A temperature sensor, attached to the container, comprising: - At least 10 feet of linear sealed conduit, which is disposed within the storage space; - A fluid, the fluid being disposed within the pipe; and - A pressure sensor, attached to the pipe, for sensing when the pressure of the fluid within the pipe exceeds a predetermined pressure. The pressure sensor is operatively connected to the valve such that the valve opens in response to a pressure sensed by the pressure sensor exceeding a predetermined pressure.

61. The assembly as claimed in claim 60, wherein, The pressure sensor includes a rupture disc.

62. The assembly as claimed in claim 60, wherein, The containers include ISO containers.

63. A double-walled safety hose, the double-walled safety hose comprising: External hose; An internal hose is disposed inside the external hose and configured to transfer pressurized fluid from a first end of the internal hose to a second end of the internal hose through its internal space. An external space, which is defined between the internal hose and the external hose; as well as A pressure relief valve is operatively connected to the external space and configured to discharge fluid from the external space if the pressure in the external space exceeds a predetermined pressure.

64. The double-walled safety hose of claim 63 further includes a ventilation channel having a first end and a second end, the first end of the ventilation channel being in fluid communication with the external space, and the pressure relief valve being disposed in the ventilation channel.

65. The double-walled safety hose of claim 63, further comprising a compressor having an outlet, the compressor being fluidly connected to the external space and configured to deliver compressed fluid to the external space.

66. The double-walled safety hose as described in claim 65, wherein, The compressor includes a pressure regulating compressor configured to sense the pressure in the external space and to deliver compressed fluid to the external space when the sensed pressure in the external space drops below a set pressure.

67. The double-walled safety hose of claim 65, further comprising a fluid source operatively connected to the inlet of the compressor.

68. The double-walled safety hose as described in claim 63, wherein, The pressure relief valve includes a single-use rupture disc.

69. The double-walled safety hose of claim 63 further includes a gas sensor positioned to sense the presence of gas in the external space, the gas being conveyed through the internal space.

70. A system for transmitting compressed gas, the system comprising: A first channel, the first channel having a first inlet and a first outlet, the first channel having a first rated pressure and an inner diameter of less than 2 inches; as well as A second channel, having a second inlet and a second outlet, the second outlet being connected to the first channel via a flow control mechanism that prevents fluid from flowing from the first channel into the second channel, the second channel having a second rated pressure lower than the first rated pressure, and the second channel having an inner diameter exceeding 2 inches. The flow control mechanism includes a check valve or a pressure regulating valve.

71. The system of claim 70, wherein, The flow control mechanism includes a pressure regulating valve disposed between the second outlet and the first channel, the pressure regulating valve being configured to close when the pressure in the first channel exceeds a predetermined pressure.

72. The system of claim 71, further comprising a check valve that separates the pressure regulating valve from the first channel.

73. The system of claim 72 further includes an additional check valve disposed between the pressure regulating valve and the second outlet, the additional check valve preventing fluid from flowing from the pressure regulating valve into the second passage.

74. The system of claim 70, further comprising: A third channel extends from the second channel to the first channel, and the third channel has a third inlet and a third outlet; and A compressor is disposed along the third channel and is configured to compress gas received from the second channel and deliver the resulting compressed gas to the first channel.

75. The system of claim 74, further comprising a check valve disposed in the third channel and preventing fluid from flowing from the first channel through the third channel into the second channel.

76. A method for supplying hydrogen to an oxygen-consuming device, the method comprising: Hydrogen is transported from the source to the oxygen-consuming device via a channel; Heat is transferred from the air separation unit to the hydrogen in the channel; To expand the hydrogen in the channel; and The expansion is used to generate electricity, which is then used to power the air separation unit.

77. The method of claim 75, further comprising: Oxygen is separated from the air via the air separation unit, and the separated air is delivered to the oxygen-consuming device.

78. The method of claim 75, wherein, The source includes a cryogenic compressed hydrogen source.

79. A method for generating cryogenic compressed hydrogen, the method comprising: Hydrogen is received from a hydrogen source at a cryogenic compressed hydrogen generator; Liquid nitrogen from the air separation unit is received at the cryogenic compressed hydrogen generator; The received liquid nitrogen is used to cryogenically compress the received hydrogen in the cryogenic hydrogen generator.

80. The method of claim 79, further comprising: Oxygen is transferred from the air separation unit to the oxygen-consuming equipment for its use; as well as Hydrogen is transferred from the hydrogen source to the oxygen-consuming device for its use.

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