Compressed gas storage and transportation

Abstract

A split stream cooling system splits a first gas stream into second and third streams, expansion cools the third stream, and then passes the second and third streams through a heat exchanger to transfer heat from the second stream to the third stream. Consequently, pressure in the third stream is converted into cooling of the second stream. A vehicle transports cryo- compressed hydrogen in a glass-reinforced storage vessel whose strength is increased by the cold temperature of the hydrogen. The cryo-compressed hydrogen may be transported within an insulated space that is cooled by a liquid nitrogen cooling system. Liquid nitrogen may be used as a ballast within the storage vessel. Various systems and methods safely store and transport compressed flammable or dangerous fluids, e.g., by controlling ventilating air exchange rates, transferring gas via a double-walled transfer hose, or sensing flames with a tubing-based temperature sensor.

Description

COMPRESSED GAS STORAGE AND TRANSPORTATIONCROSS REFERENCE

[0001] This application claims the benefit of priority from U.S. Provisional Patent Application No. 63 / 468,881, filed May 25, 2023, titled “COMPRESSED GAS STORAGE AND TRANSPORTATION,” the entire contents of which are hereby incorporated by reference herein.BACKGROUND1. Field of the Invention

[0002] Various embodiments relate generally to vehicles for transporting gases such as compressed natural gas or hydrogen.2. Description of Related Art

[0003] Gaseous fuels, such as natural gas, are typically transported by pipeline, although there are users of natural gas that periodically require natural gas supply in excess of the supply available through existing pipelines. In addition, there are areas in which natural gas service via pipeline is not available at all, due to remoteness, the high cost of laying pipelines, or other factors. For such areas, natural gas can be transported via CNG vessels, for example as described in PCT Publication Nos. WO2014 / 031999 and 2018 / 144328, the entire contents of each of which are hereby incorporated by reference.

[0004] Natural gas and hydrogen are conventionally transported across waterways (e.g., rivers, lakes, gulfs, seas, oceans) in liquid natural gas (LNG) and liquid hydrogen (LH) form. However, LNG and LH require complicated and expensive liquefaction plants and special handling on both the supply and delivery side. LNG and LH also require regasification upon delivery, which involves using substantial amounts of heat and complex cryogenic heat exchangers as well as cryogenic delivery / stor ge equipment.SUMMARY

[0005] One or more non-limiting embodiments provide a method of cooling a compressed gas. The method includes splitting a first stream of compressed gas into second and third streams; expansion cooling the third stream; and downstream from where the third stream is expansioncooled, passing the third stream and second stream through a heat exchanger, which transfers heat from the second stream to the third stream.

[0006] According to one or more of these embodiments, the heat exchanger comprises a first heat exchanger, and the method further comprises, downstream from where the third stream exits the first heat exchanger, passing the third stream and first stream through a second heat exchanger, which transfers heat from the first stream to the third stream.

[0007] According to one or more of these embodiments, the method includes actively cooling the first stream after the first stream exits the second heat exchanger.

[0008] According to one or more of these embodiments, said expansion cooling comprises JT cooling.

[0009] According to one or more of these embodiments, said expansion cooling comprises passing the third stream through a turbo expander.

[0010] According to one or more of these embodiments, the method includes controlling a flow rate of the second stream relative to the third stream so as to ensure that a temperature of the second stream is within a predetermined temperature range upon exiting the heat exchanger.

[0011] According to one or more of these embodiments, the method includes compressing the third stream downstream from the heat exchanger to form a fourth stream; and combining the fourth stream and a fifth stream to form the first stream.

[0012] One or more embodiments provide a system for cooling a compressed gas. The system includes a compressed gas inlet for receiving compressed gas; a heat exchanger; a splitter; an expansion cooler; a compressed gas outlet; a first passageway extending from the inlet to the splitter; a second passageway extending sequentially from the splitter, through the heat exchanger, and to the compressed gas outlet; and a third passageway extending sequentially from the splitter, through the expansion cooler, and through the heat exchanger.

[0013] According to one or more of these embodiments, the system includes a refrigeration unit disposed in the first passageway.

[0014] According to one or more of these embodiments: the heat exchanger comprises a first heat exchanger; the system further comprises a second heat exchanger; the first passageway passes through the second heat exchanger; and the third passageway passes sequentially from the splitter, through the expansion cooler, through first heat exchanger, and then through the second heat exchanger.

[0015] One or more embodiments provides a combination for transporting cryo-compressed hydrogen. The combination includes: a vehicle; an insulated space supported by the vehicle; a glass- reinforced storage vessel disposed in the insulated space, the storage vessel defining an interior space; and cryo-compressed hydrogen stored within the vessel. According to one or more of these embodiments, a pressure within the vessel is between 900 and 10,000 psig and a temperature within the vessel is between 60 and 210 K.

[0016] According to one or more of these embodiments, a density of the cryo-compressed hydrogen within the vessel is at least 1.0 lbm / ft3.

[0017] According to one or more of these embodiments, the cryo-compressed hydrogen occupies at least 75% of a volume of the vessel.

[0018] According to one or more of these embodiments, the vehicle comprises a ship.

[0019] According to one or more of these embodiments, the combination includes a pressure relief valve operatively connected to the vessel and configured to vent gas from within the vessel to an ambient environment outside the vehicle if the pressure exceeds a predetermined pressure.

[0020] According to one or more of these embodiments, the pressure relief valve comprises an emergency burst disc.

[0021] According to one or more of these embodiments, the combination includes a pressure relief valve operatively connected to the insulated space and configured to vent gas from within the insulated space to an ambient environment outside the vehicle if a pressure within the insulated space exceeds a predetermined pressure.

[0022] According to one or more of these embodiments, the predetermined pressure is between 0.1 and 3.0 psi relative to a pressure of the ambient environment.

[0023] According to one or more of these embodiments, the pressure relief valve comprises an emergency burst hatch.

[0024] According to one or more of these embodiments, the vessel comprises a composite reinforced material.

[0025] According to one or more of these embodiments, the vessel comprises glass that is stronger at the temperature than at 273 K.

[0026] According to one or more of these embodiments, the vessel comprises a storage cylinder with a liner, wherein the liner comprises HDPE, PA-6, UHMWPE or 316L stainless steel.

[0027] According to one or more of these embodiments, the combination includes an excess flow valve operatively connected to the vessel.

[0028] According to one or more of these embodiments, the vehicle may be a ship, a wheeled vehicle (e.g., truck and trailer, a railcar), or a barge.

[0029] One or more embodiments provide a combination for transporting cryo-compressed hydrogen. The combination includes: a vehicle; an insulated space supported by the vehicle; liquid nitrogen disposed in the insulated space; a storage vessel disposed in the insulated space, the storage vessel defining an interior space; and cryo-comprcsscd hydrogen stored within the vessel.According to one or more of these embodiments, a pressure within the vessel is between 900 and 10,000 psig and a temperature within the vessel is between 60 and 210 K.

[0030] According to one or more of these embodiments, the liquid nitrogen disposed in the insulated space is disposed outside the vessel.

[0031] According to one or more of these embodiments, the combination includes: a nitrogen liquefaction system supported by the vehicle and configured to liquify gaseous nitrogen; a liquid nitrogen passageway operatively connecting the liquefaction system to the insulated space and configured to transfer liquid nitrogen from the liquefaction system to the insulated space; and a nitrogen return passageway operatively connecting the insulated space to the liquefaction system and configured to transfer gaseous nitrogen from the insulated space to the liquefaction system so that the liquefaction system can liquify gaseous nitrogen received from the insulated space via the nitrogen return passageway.

[0032] According to one or more of these embodiments, the liquefaction system is configured to maintain a pressure within the insulated space of 0.1 to 2.0 psig relative to an ambient pressure outside the vehicle.

[0033] According to one or more of these embodiments, the insulated space comprises a depression shaped and configured to collect and retain liquid nitrogen.

[0034] According to one or more of these embodiments, the combination includes a nitrogen generator configured to collect and isolate nitrogen from ambient air and provide isolated nitrogen to the 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.

[0035] According to one or more of these embodiments, the nitrogen generator comprises a compressor that is configured to compress ambient air, and a pressure swing absorption device configured to separate nitrogen out of compressed air.

[0036] According to one or more of these embodiments, the storage vessel comprises a glass -reinforced storage vessel.

[0037] According to one or more of these embodiments, the liquid nitrogen disposed in the insulated space is disposed in the interior space.

[0038] According to one or more of these embodiments, the vessel includes a gas port that fluidly connects to an upper portion of the interior space, and a liquid port that fluidly connects to a lower portion of the interior space.

[0039] According to one or more of these embodiments, the combination includes a baffle disposed within the vessel.

[0040] According to one or more of these embodiments, the combination includes a float in the interior space, the float being vertically movable within the interior space, the float separating the interior space into an upper portion above the float and a lower portion below the float, the float having a density higher than the cryo-compressed hydrogen and lower than the liquid nitrogen.

[0041] According to one or more of these embodiments, the combination includes: a liquid nitrogen storage container; a liquid nitrogen supply passageway connecting the container to the vessel; and a pump positioned and configured to pump liquid nitrogen from the container into the interior space.

[0042] According to one or more of these embodiments, the pump is configured to pump liquid nitrogen into the interior space during unloading of the cryo-compressed hydrogen from the vessel so as to displace cryo-compressed hydrogen within the interior space and facilitate substantially isothermal and isobaric unloading of the cryo-compressed hydrogen from the vessel.

[0043] According to one or more of these embodiments, the combination includes: a liquid nitrogen return passageway connecting the liquid nitrogen storage container to the interior space; and a valve disposed in the liquid nitrogen return passageway, the valve having an open state in which liquid nitrogen can flow from the interior space to the container, the valve having a closed state preventing liquid nitrogen from flowing from the interior space to the container.

[0044] According to one or more of these embodiments, the valve comprises a pressure- regulated valve configured to open when a pressure in the vessel exceeds a predetermined pressure.

[0045] According to one or more of these embodiments, the valve is configured to facilitate substantially isobaric loading of the vessel with cryo-compressed hydrogen.

[0046] One or more embodiments provide a method of transporting cryo-compressed hydrogen using a vehicle with an insulated space and a storage vessel disposed within the insulated space, the storage vessel defining an interior space. The method includes: cooling a temperature within the interior space to between 77 and 90 K; pressurizing the interior space to a pressure of between 900 and 10,000 psig (and / or between 2,000 and 7,500 psig); and while the temperature is between 60 and 210 K (and / or bctwccn77 and 90 K) and the pressure is between 900 and 10,000 psig (and / or between 2,000 and 7,500 psig), transferring cryo-compressed hydrogen into the interior space.

[0047] According to one or more of these embodiments, said cooling occurs while the pressure within the interior space is less than 300 psig.

[0048] According to one or more of these embodiments, said cooling comprises disposing liquid nitrogen in the insulated space outside of the vessel while the pressure within the interior space is less than 300 psig.

[0049] One or more embodiments provide a method of making a storage vessel for storing compressed fluids. The method includes: inserting an expandable scaffolding through a hole in a liner; radially expanding the scaffolding within an interior space inside the liner so as to mechanically support the liner; wrapping a composite reinforcement around the liner while the scaffolding is disposed within the liner, wherein the composite reinforcement comprising glass and resin; curing the resin; collapsing the scaffolding; and removing the mechanical support from the liner via the hole in the liner.

[0050] According to one or more of these embodiments, the liner comprising HDPE, PA-6, UHMWPE, or 316L stainless steel.

[0051] According to one or more of these embodiments, the composite reinforcement comprises at least 60% fiber glass and at least 10% resin.

[0052] According to one or more of these embodiments, the composite reinforcement comprises at least 10% insulation.

[0053] According to one or more of these embodiments, the insulation comprises perlite.

[0054] According to one or more of these embodiments, the composite reinforcement comprises a fire retardant.

[0055] According to one or more of these embodiments, the liner has an expansion joint.

[0056] According to one or more of these embodiments, the expansion joint comprises corrugations in the liner, said corrugations facilitating expansion and contraction of the liner.

[0057] According to one or more of these embodiments, the vessel comprises a cylinder that is elongated in an axial direction of the cylinder, and wherein the expansion joint facilitates expansion and contraction of the liner along the axial direction.

[0058] According to one or more of these embodiments, the vessel comprises a cylinder that is elongated in an axial direction of the cylinder, and wherein the wrapping occurs while the axial direction is within 10 degrees of a vertical orientation.

[0059] According to one or more of these embodiments, said wrapping comprises: wrapping the liner with a first sub-layer of glass stiffening material and a first sub-layer of resin; curing the first sub-layer of resin; and wrapping a second sub-layer of glass stiffening material and a second sub-layer of resin over top of the first sub-layer of glass stiffening material and first sub-layer of resin.

[0060] One or more embodiments provide a combination for transporting compressed flammable gas, the combination comprising: a vehicle; an storage space supported by the vehicle; a gas storage vessel disposed within the storage space and defining an interior space, the storage vessel having a pressure relief valve configured to release gas from the within the interior space into the insulated storage space if a pressure within the interior space exceeds a predetermined pressure; a compressed gas stored in the interior space of the storage vessel; a gas sensor disposed within the storage space and configured to detect when a concentration of the gas within the storage space outside of the storage vessel exceeds a predetermined concentration; at least one fan connected to the storage space and configured to exchange air between the storage space and an ambient 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 a rate of air exchange between the storage space and ambient environment in response to sensing that the gas within the storage hold outside of the storage vessel exceeds the predetermined concentration.

[0061] According to one or more of these embodiments, the combination includes a plurality of additional gas storage vessels disposed within the storage space, each of the plurality of additional gas storage vessels having an interior space and a pressure relief valve configured to release gas from within the respective one of the plurality of additional gas storage vessels into thestorage space if a pressure within the interior space of the respective storage vessel exceeds a predetermined pressure.

[0062] According to one or more of these embodiments, the interior space of each of the plurality of storage vessels is fluidly isolated from each other.

[0063] According to one or more of these embodiments, the at least one fan comprises at least one inflow fan positioned to blow ambient air from the ambient environment into the insulated storage hold, and at least one exhaust fan positioned to blow air from within the insulated storage hold to the ambient environment.

[0064] One or more embodiments provide a combination for transporting compressed flammable gas, the combination comprising: a container defining a storage space; a compressed-gas storage vessel disposed within the storage space; a pressure-relief valve connected to the vessel so as to vent pressurized gas stored within the vessel when the valve is opened; and a temperature sensor attached to the container.

[0065] According to one or more of these embodiments, the temperature sensor includes: at least 10 linear feet of sealed tubing disposed within the storage space; fluid disposed within the tubing; and a pressure sensor attached to the tubing to sense when a pressure of the fluid within the tubing exceeds a predetermined pressure. According to one or more of these embodiments, the pressure sensor is operatively connected to the valve so that the valve opens in response to a pressure sensed by the pressure sensor exceeding the predetermined pressure.

[0066] According to one or more of these embodiments, the pressure sensor comprises a burst disc.

[0067] According to one or more of these embodiments, the container comprises an ISO container.

[0068] One or more embodiments provide a double-walled safety hose comprising: an outer hose; an inner hose disposed inside the outer hose, the inner hose being configured to transfer a pressurized fluid through an inner space of the inner hose from a first end of the inner hose to a second end of the inner hose; an outer space defined between the inner and outer hoses; and a pressure relief valve operatively connected to the outer space and configured to vent fluid from the outer space if a pressure in the outer space exceeds a predetermined pressure.

[0069] According to one or more of these embodiments, the double-walled safety hose includes a vent passageway having first and second ends, a first end of the vent passageway beingin fluid communication with the outer space, the pressure relieve valve being disposed in the vent passageway.

[0070] According to one or more of these embodiments, the double-walled safety hose includes a compressor with an outlet fluidly connected to the outer space and configured to transfer compressed fluid into the outer space.

[0071] According to one or more of these embodiments, the compressor comprises a pressure-regulated compressor configured to sense a pressure in the outer space, and transfer compressed fluid into the outer space when a sensed pressure in the outer space falls below a set pressure.

[0072] According to one or more of these embodiments, the double-walled safety hose includes a source of fluid operatively connected to an inlet of the compressor.

[0073] According to one or more of these embodiments, the pressure relief valve comprises a single-use burst disk.

[0074] According to one or more of these embodiments, the double-walled safety hose includes a gas sensor positioned to sense the presence in the outer space of a gas that is being transferred through the inner space.

[0075] One or more embodiments provide a system for transferring compressed gas. The system includes: a first passageway having a first inlet and a first outlet, the first passageway having a first pressure rating and an internal diameter of less than 2 inches; and a second passageway having a second inlet and a second outlet, the second outlet being connected to the first passageway via a flow control mechanism that prevents fluid flow from the first passageway into the second passageway, the second passageway having a second pressure rating that is lower than the first pressure rating, the second passageway having an internal diameter of over 2 inches. According to one or more of these embodiments, the flow control mechanism comprises a check valve or a pressure-regulated valve.

[0076] According to one or more of these embodiments, the flow control mechanism comprises a pressure-regulated valve disposed between second outlet and the first passageway, the pressure-regulated valve being configured to close when a pressure within the first passageway exceeds a predetermined pressure.

[0077] According to one or more of these embodiments, the system includes a check valve separating the pressure -regulated valve from the first passageway.

[0078] According to one or more of these embodiments, the system includes an additional check valve disposed between the pressure-regulated valve and second outlet, the additional check valve preventing fluid flow from the from the pressure-regulated valve to the second passageway.

[0079] According to one or more of these embodiments, the system includes: a third passageway extending from the second passageway to the first passageway, the third passageway having a third inlet and a third outlet; a compressor disposed along the third passageway and configured to compress gas received from the second passageway and deliver a resulting compressed gas to the first passageway.

[0080] According to one or more of these embodiments, the system includes a check valve disposed in the third passageway and preventing fluid flow from the first passageway into the second passageway via the third passageway.

[0081] One or more of these and / or other aspects of various embodiments of the present invention, as well as the methods of operation and functions of the related elements of structure and the combination of pails and economies of manufacture, will become more apparent upon consideration of the following description and the appended claims with reference to the accompanying drawings, all of which form a part of this specification, wherein like reference numerals designate corresponding parts in the various figures. In one embodiment, the structural components illustrated herein are drawn to scale. It is to be expressly understood, however, that the drawings are for the purpose of illustration and description only and are not intended as a definition of the limits of the invention. In addition, it should be appreciated that structural features shown or described in any one embodiment herein can be used in other embodiments as well. As used in the specification and in the claims, the singular form of “a”, “an”, and “the” include plural referents unless the context clearly dictates otherwise.

[0082] All closed-ended (e.g., between A and B) and open-ended (greater than C) ranges of values disclosed herein explicitly include all ranges that fall within or nest within such ranges. For example, a disclosed range of 1-10 is understood as also disclosing, among other ranges, 2-10, 1-9, 3-9, etc. Similarly, where multiple parameters (e.g., parameter C, parameter D) arc separately 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).BRIEF DESCRIPTION OF THE DRAWINGS

[0083] For a better understanding of various embodiments as well as other objects and further features thereof, reference is made to the following description which is to be used in conjunction with the accompanying drawings, where:

[0084] FIG. 1 is a diagrammatic view of a split stream gas cooling system 100 according to one or more embodiments.

[0085] FIG. 2 is a diagrammatic view of a cryo-compressed hydrogen transportation vehicle according to one or more embodiments.

[0086] FIG. 3 is a hydrogen phase diagram.

[0087] FIG. 4 is a diagrammatic view of a cryo-compressed hydrogen transportation vehicle according to one or more embodiments.

[0088] FIG. 5 is a cut-away view of a cryo-compressed hydrogen storage vessel according to one or more embodiments.

[0089] FIG. 6 is a cut-away end view showing a manufacturing step during the manufacture of a cryo-compressed hydrogen storage vessel according to one or more embodiments.

[0090] FIG. 7 is a diagrammatic view of an air exchange system for a storage space for a compressed flammable or otherwise dangerous gas.

[0091] FIG. 8 is a diagrammatic view of a temperature sensor for a storage container according to one or more embodiments.

[0092] FIG. 9 is an end cross-sectional view of a double-walled hose according to one or more embodiments.

[0093] FIG. 10 is a diagrammatic view of the double-walled hose of FIG. 9.

[0094] FIGS. 11-12 are diagrammatic views of dual pressure gas transfer systems according different embodiments.

[0095] FIG. 13 is a diagrammatic view of a split stream gas cooling system 7000 according to one or more embodiments.

[0096] FIG. 14 is a diagrammatic view of a refrigeration system 310b of the system 7000 shown in FIG. 14.

[0097] FIG. 15 is a diagrammatic view of a system 7500 for delivering hydrogen to a steel mill according to one or more embodiments.

[0098] FIG. 16 is a diagrammatic view of a system 8000 for generating cryo-compressed hydrogen.DETAILED DESCRIPTION OF EXEMPLARY EMBODIMENTS

[0099] Split Stream Gas Cooling

[0100] As shown in FIG. 1, one or more embodiments provide a split stream cooling system 100 and method for splitting a first compressed gas stream 110 into a second compressed gas stream 120 and a third compressed gas stream 130, wherein the third stream 130 is used to cool the second compressed gas stream 120. The system trades a pressure drop in the third stream 130 for a temperature drop in the second stream 120, preferably without sacrificing pressure in the second stream.

[0101] As shown in FIG. 1, a compressed gas passageway 200 leads sequentially from a gas inlet 210, through junctions 300, 330, through a heat exchanger 280, through an active refrigerator 310, and to a splitter 220 (e.g., a Y or T connection). A passageway 230 leads sequentially from the splitter 220, through a heat exchanger 270, and to a cold, high-pressure gas outlet 240. A passageway 250 leads sequentially from the splitter 220 through an expansion cooler 260, the heat exchanger 270, the heat exchanger 280, a compressor 290, and finally back to the junction 300 in the passageway 200. A passageway 320 leads from the junction 330 to a warm, high-pressure gas outlet 340.

[0102] In the illustrated embodiment, the junction 330 is downstream from the junction 300, but their relative positioning can be switched without deviating from the scope of various embodiments.

[0103] The refrigerator 310 may comprise any type of active refrigerator (e.g., a phasechange refrigerator based on freon, HFA, or other refrigerants). The refrigerator 310 pulls heat out of a gas stream 110 passing through the passageway 200 to cool the gas stream 110. However, according to various alternative embodiments, the refrigerator 310 may be omitted without deviating from the scope of various embodiments of the invention.

[0104] In the illustrated embodiment, the refrigerator 310 cools the first stream 110. However, according to alternative embodiments, the refrigerator could alternatively be disposed in the passageway 230 between the splitter 220 and heat exchanger 270 so as to cool the second stream

[0105] In the embodiment illustrated in FIG. 1, the refrigerator 310 is a single stage refrigerator 310. However, according to alternative embodiments, the refrigerator 310 may comprise a multi-stage refrigerator 310, as illustrated in FIG. 13. As shown in FIG. 13, the refrigerator 310 comprises a first stage refrigerator 310a and a second stage refrigerator 310b.

[0106] According to one or more embodiments and as shown in FIG. 13, the first stage refrigerator 310a provides pre-cooling and cools the process fluid stream 110 to a temperature between -25 and -45 °F. According to various embodiments, the refrigerator 310a may use a refrigerant such as propane in its coolant loop.

[0107] According to one or more embodiments and as shown in FIG. 13, the second stage refrigerator 310b further cools the process fluid stream 110. According to one or more embodiments, the second stage refrigerator 310b is a deep cooling cycle refrigerator, which cools the process fluid stream 110 to a temperature between -100 and -370 °F. According to various embodiments, this two-stage cooling may help to facilitate a process fluid temperature at the outlet 240 of around -320 °F.

[0108] As shown in FIG. 14, the refrigerator 310b may comprise a cooling loop 7100. The refrigerant in the loop 7100 passes sequentially through a compressor 7110, heat exchanger / refrigerator 7120, expander 7130, and heat exchanger 7140. The compressor 7110 compresses the refrigerant, which raises its temperature. The heat exchanger 7120 may itself be an active refrigeration system (e.g., air or pre-cool cycle), and is designed to remove heat from the refrigerant. The compressed and cooled refrigerant then passes through an expander, which cools the refrigerant before the refrigerant passes through the heat exchanger 7140, where heat is transferred from the process fluid stream 110 to the refrigerant in the loop 7140, thereby cooling the process fluid stream 110.

[0109] According to various embodiments, control valves or other devices may be disposed in any of the passageways 200, 230, 250, 320, 380 so as to control the flow rate through such passageways. Controlling the relative flow rates of the different streams may help to control the outlet temperature of the streams passing through the heat exchangers 270, 280 to better match a target temperature (e.g., of the stream 120 at the outlet 240).

[0110] According to various embodiments, the expansion cooler 260 may be, for example, an orifice, turbo-expander 260a (see FIG. 13), or J-T expander. If a turbo-expander 260a is used (as shown in FIG. 13), the turbo-expander 260a may optionally be used to recover energy from the gasstream 130. According to one or more embodiments, a turbo-expander 260a is used in embodiments in which a J-T expander would be inefficient or ineffective (e.g., if the temperature of the stream 130 passing through the cooler 260 is such that the stream 130 has a J-T coefficient that is near 0 or negative). According to various embodiments, the energy recovered from the expander 260a may be used to drive the compressor 290 and / or compressor 7200 (see FIG. 13). The energy transfer from the expander 260a to a compressor(s) 290, 7200 may be by way of a mechanical connection (e.g., an output shaft of the expander 260a being connected either directly or via a gearbox or transmission to an input shaft of the comprcssor(s) 290, 7200), an electrical connection (e.g., by using the output shaft of the expander 260a to drive an electric generator, whose generated electricity is provided to a motor that drives the compressor(s) 280, 7200).

[0111] According to one or more embodiments, the expansion cooler 260 has a variable flow rate with the flow rate being controlled by a temperature sensor (and / or a pressure sensor used to assess temperature), which senses a temperature of the second stream 120 downstream from the heat exchanger 270 (e.g., between the heat exchanger 270 and outlet 240). According to various embodiments, the flowrate is automatically controlled so as to avoid overcooling. According to various embodiments, the temperature-controlled expansion cooler 260 is configured to increase a flow rate of the third stream 130 when a temperature in the second stream 120 downstream from the cooler 260 exceeds a preset temperature. Additionally and / or alternatively, the temperature- controlled expansion cooler 260 is configured to adjust the flow rate of the third stream 130 so as to maintain a temperature of the second stream 120 downstream from the cooler 260 within a predetermined temperature parameter, e.g., (a) at least -150, -125, -100, -90, -80, -70, -60, -50, -40, -30, -20, -10, and / or 0 degrees F, (b) less than 40, 30, 20, 10, 0, -10, -20, -30, -40, -50, -60, -70, -80- , -90, and / or -100 degrees F, and / or (c) between any two such values (e.g., by between -150 and 40 degrees F, by between -60 and -40 degrees F).

[0112] According to one or more embodiments, the system 100 optionally includes a bypass passageway 380, which connects to the passageway 200 upstream and downstream from the heat exchanger 280. A bypass valve 390 is disposed in the passageway 380. According to various embodiments, the valve 290 is a temperature-controlled valve that selectively opens and closes the valve 390 based on a temperature sensor (not shown) that senses a temperature of the third stream 130 downstream from the heat exchanger 280. According to various non-limiting embodiments, the temperature-controlled valve selectively opens so as to cause a portion of the stream 110 to bypassthe heat exchanger in order to avoid overcooling of the stream 110 (and downstream split stream 130).

[0113] The passageways 200, 230, 250, 320, 380 may comprise any type of suitable passageways for transferring gas at the temperature and pressures of the gases passing through such passageway(s). The passageways may be rigid (e.g., metal pipes), flexible (e.g., hoses), and / or a mixture of rigid and flexible passageways.

[0114] The various inlets and outlets 210, 340, 240 may comprise detachable connectors or may be otherwise connected (e.g., via welded joints, threaded joints, etc.) to gas sources and destinations.

[0115] Hereinafter, operation of the system 100 is described with reference to FIG. 1.

[0116] The inlet 210 leads from a source of compressed gas. According to various embodiments, an incoming source gas stream 350 received at the inlet 210 has a pressure of (1) at least 250, 300, 350, 400, 450, 500, 1000, 1500, 2000, 2500, 3000, 3500, 4000, 4500, 5000, 6000, 7000, 8000, 9000, 10000, 11000, and / or 12000 psig, (2) at most 14000, 12000, 10000, 8000, 6500, 5000, 4500, 4000, 3500, 3000, 2000, and / or 1500 psig, and / or (3) any pressure between any two such values (e.g., between 250 and 14000 psig, between 1500 and 4500 psig). According to various embodiments, the source gas stream 350 has a temperature of (a) at least -40, -20, 0, 10, 20, 30, 40, 50, 60, 70, 80, 90, 100, 110 and / or 120 °F, (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 °F, and / or (c) between any two such temperatures (e.g., between 0 and 200 °F, between 60 and 150 °F, between 80 and 140 °F). According to various embodiments, a compressor (not shown) disposed upstream from the inlet 210 may compress and heat gas, which results in the incoming source gas stream 350 having a high pressure and temperature.

[0117] According to one embodiment, the compressed gas received at the inlet 210 is compressed natural gas (CNG). However, according to various alternative embodiments, the compressed gas received at the inlet 210 may comprise any gas with a positive J-T coefficient where the gas stream 130 passes through the expansion cooler 260 (e.g., air, nitrogen, argon, carbon dioxide). According to an alternative embodiment, the compressed gas comprises hydrogen at temperatures below 200 K.

[0118] The incoming source stream 350 mixes with the third stream 130 at the junction 300 to form the first stream 110. Such mixing is preferable for embodiments in which heat is extractedfrom the stream 130 between the compressor 290 and junction 300 (e.g., via an active or passive refrigeration system (not shown) disposed in the passageway between the compressor 290 and junction 300). However, according to various alternative embodiments (not shown), the third stream 130 never mixes back into the source stream 350, in which case the third stream 130 is not recirculated. Rather, the third stream 130 can alternatively lead to a low-pressure outlet.

[0119] According to various embodiments, a fourth stream 360 branches off from the junction 330 to provide high pressure gas to the outlet 340. According to various embodiments, the fourth stream 360 comprises a part of the source stream 350 and a part of the third stream 130, which has 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 part of the source stream 350.

[0120] According to various embodiments, the fourth stream 360 is provided to the outlet 340 at: i) a pressure of (1) at least at least 250, 300, 350, 400, 450, 500, 1000, 1500, 2000, 2500, 3000, 3500, 4000, 4500, 5000, 6000, 7000, 8000, 9000, 10000, 11000, and / or 12000 psig, (2) at most 14000, 12000, 10000, 8000, 6500, 5000, 4500, 4000, 3500, 3000, 2000, and / or 1500 psig, and / or (3) any pressure between any two such values (e.g., between 250 and 14000 psig, between 1500 and 4500 psig); and / or ii) a temperature of (a) at least -40, -20, 0, 10, 20, 30, 40, 50, 60, 70, 80, 90, 100, 110 and / or 120 °F, (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 °F, and / or (c) between any two such temperatures (e.g., between 0 and 200 °F, between 60 and 150 °F, between 80 and 140 °F).

[0121] According to various embodiments, the first stream 110 enters the heat exchanger 280 at a higher temperature than the third stream 130 enters the heat exchanger 280. 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 about 120 degrees F and exits the heat exchanger 280 at 60 degrees F. According to various embodiments, the third stream 130 enters the heat exchanger 280 at -20 degrees F and leaves the heat exchanger at 80 degrees F. However, according to various embodiments, the heat exchanger 280 may be eliminated altogether.

[0122] After exiting the heat exchanger 280, the first stream 110 passes through the 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 degrees F, (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 degrees F, and / or (c) between any two such values (e.g., by between 5 and 500 degrees F, by between 15 and 50 degrees F, by between 100 and 400 degrees F, by between 200 and 500 degrees F). However, according to various alternative embodiments, the refrigeration unit 310 is omitted entirely. In such embodiments, the entire system 100 may omit active refrigeration.

[0123] After leaving the refrigeration unit 310, the first stream splits into the second and third streams 120, 130 at the splitter 220. The second stream 120 then passes through the heat exchanger 270, which cools the second stream 120. The third stream 130 passes through the expansion cooler 260, which reduces both the pressure and temperature of the third stream 130, and then through the heat exchanger 270.

[0124] 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 degrees F, (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 degrees F, and / or (c) between any two such values (e.g., by between 5 and 110 degrees F, by between 40 and 90 degrees F).

[0125] 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.

[0126] According to one or more embodiments, the third stream 130 enters the heat exchanger 270 at -70 degrees F, and leaves the heat exchanger 270 at -20 degrees F. According to various embodiments, the second stream 120 enters the heat exchanger 270 at 0 degrees F and leaves the heat exchanger 270 at -40 degrees F (e.g., for one or more embodiments in which the process fluid is natural gas). The temperature of the second stream when it enters the heat exchanger 270 will depend, among other things, on whether the first stream 110 passed through the heat exchanger 280 and / or the refrigeration unit 310. In embodiments that omit the heat exchanger 280 and refrigeration unit 310 and do not remix the third stream 130 with the source stream 350, thesecond stream 120 may enter the heat exchanger 270 at approximately the same temperature and pressure as the source stream 350 entered the system 100.

[0127] According to various embodiments, the heat exchanger 270 cools the 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 degrees F, (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 degrees F, and / or (c) between any two such values (e.g., by between 5 and 110 degrees F, by between 40 and 90 degrees F).

[0128] After exiting the heat exchanger 270, the second stream 120 flows on to the cooled compressed gas outlet 240. According to various embodiments, the second stream 120 arrives at the outlet 240 at: i) a temperature 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 degrees F, (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 degrees F, and / or (c) between any two such values (e.g., between -500 and 40 degrees F, between -150 and 40 degrees F, between -60 and - 40 degrees F, between -100 and -370 degrees F); and / or ii) a pressure of (1) at least at least 250, 300, 350, 400, 450, 500, 1000, 1500, 2000, 2500, 3000, 3500, 4000, 4500, 5000, 6000, 7000, 8000, 9000, 10000, 11000, and / or 12000 psig, (2) at most 14000, 12000, 10000, 8000, 6500, 5000, 4500, 4000, 3500, 3000, 2000, and / or 1500 psig, and / or (3) any pressure between any two such values (e.g., between 250 and 14000 psig, between 1500 and 4500 psig).

[0129] According to various embodiments, the second stream 120 arrives at the outlet 240 at: i) a temperature that is colder than the source stream 350 at the inlet 210 by: (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 degrees F, (b) less than 600, 500, 400, 350, 300, 250, 200, 190, 180, 170, 160, 150, 140, 130, 120, 110, 100, 90, 80, 70, 60, and / or 50 degrees F, and / or (c) between any two such values (e.g., between 10 and 600 degrees F colder); and / orii) a pressure that deviates from a pressure of the source stream 350 at the inlet 210 by less than 5000, 4000, 3000, 2000, 1000, 900, 800, 700, 600, 500, 400, 300, 200, 100, 75, 50, 40, 30, 20, and / or 10 psi.

[0130] After exiting the heat exchanger 270, for embodiments that include the heat exchanger 280, the third stream 130 passes through the heat exchanger 280.

[0131] According to one or more embodiments, after exiting the heat exchanger 280, the third stream 130 may pass through the compressor 290, which compresses the third stream to at or near the pressure of the source stream 350. After exiting the compressor 290, the third stream 130 mixes with the source stream 350 at the junction 300. However, according to various embodiments, the compressor 290 and junction 300 are omitted such that the third stream 130 is not recirculated, and can instead be transferred on to a destination that is configured to use lower pressure gas from the third stream 130. Additionally and / or alternatively, the passageway for the stream 130 could lead to an inlet of a main compressor disposed upstream from the inlet 210, in which case the main compressor (not shown) would replace the compressor 290. That main compressor may compress both an incoming fresh stream of gas as well as the recirculated stream 130. In such an embodiment, an active or passive refrigeration system may be disposed between an outlet of the main compressor and the inlet 210 to remove heat from the gas stream before that gas stream enters the inlet 210.

[0132] According to one or more embodiments, the second stream 120 can be cooled, relative to a temperature of the source stream 350, without the use of an active refrigeration unit 310.

[0133] According to various embodiments, the second stream 120 can be cooled without a significant pressure drop in the second stream 120.

[0134] FIGS. 13-14 illustrate an alternative split stream cooling system 7000 according to one or more embodiments.

[0135] As shown in FIG. 13, a compressor 7200 is disposed in the passageway 200 between the inlet 210 and junction 300 to further compress the incoming process fluid stream 350. The compressor 7200 overpressures the gas stream 110.

[0136] As shown in FIG. 13, the passageway 200 splits downstream from the compressor 290 with one branch leading to the junction 300 and a second branch leading to the passageway 200 at a location between the inlet 210 and compressor 7200. This enables either single-stagecompression of recycled fluid through just the compressor 290, or multi-stage compression of the recycled fluid through both compressors 7200, 290.

[0137] As shown in FIG. 13, an expansion cooler (e.g., turbo-expander 7210 and / or J-T expander 7220) is disposed in the passageway 230 between the heat exchanger 270 and outlet 240 to further cool the stream 120 before reaching the outlet 240. According to one or more embodiments and as shown in FIG. 13, if the expansion cooler includes both a turbo-expander 7210 and a I-T expander 7220, the two can be disposed in parallel via the use of a parallel passageway 7230. According to various embodiments, the J-T valve 7220 is used if the process fluid is hydrogen and its temperature is low enough to have a sufficiently positive J-T coefficient such that passing the stream 120 through the J-T valve 7220 cools the stream 120. According to various nonlimiting embodiments, the J-T valve 7220 is used if the hydrogen process fluid stream 120 temperature is below -250 °F when it reaches the expansion cooler.

[0138] According to various embodiments, the combined use of an upstream overpressure boost compressor 7200 and a downstream expansion cooler 7210, 7220 enables the system 7000 to provide a colder gas stream 120 at the outlet 240 than in one or more embodiments without the use of such over-pressure. The additional and / or alternative use of a multi-stage refrigerator 310 may facilitate further cooling to very low temperatures. These additional cooling methods are well suited for embodiments in which the working fluid is very low temperature hydrogen because hydrogen has a beneficially higher J-T coefficient at very low temperatures.

[0139] According to one or more embodiments of the system 7000, the second stream 120 enters the heat exchanger 270 at 0 degrees F and leaves the heat exchanger 270 at -40 degrees F (e.g., for an embodiment in which the process fluid is natural gas). The temperature of the second stream when it enters the heat exchanger 270 will depend, among other things, on whether the first stream 110 passed through the heat exchanger 280 and / or the refrigeration unit 310. In embodiments that omit the heat exchanger 280 and refrigeration unit 310 and do not remix the third stream 130 with the source stream 350, the second stream 120 may enter the heat exchanger 270 at approximately the same temperature and pressure as the source stream 350 entered the system 100.

[0140] According to one or more embodiments of the system 7000 in which the process fluid is hydrogen and a multi-stage refrigeration system 310 is used, the first stream 110 leaves the first stage refrigerator 310a (e.g., a propane-based refrigerator) at about -40 degrees F, and leavesthe second stage refrigerator 310b (e.g., a nitrogen or mixed refrigerant-based refrigerator) at about -320 degrees F.

[0141] Cryo-Compressed Hydrogen Transportation System And Method

[0142] One or more embodiments provide a more efficient and / or less expensive system for transporting hydrogen. By transporting hydrogen in a cryo-compressed state, hydrogen can advantageously be transported at densities that approach the density of liquid hydrogen, but without the need for complicated and expensive liquefaction plants. As explained below, according to various embodiments, glass -reinforced hydrogen storage containers facilitate the efficient storage of cry-compressed hydrogen because the vessel-reinforcing glass is stronger at cryo-compressed hydrogen temperatures than glass would be at higher (e.g., ambient) temperatures. As explained below, according to various embodiments, the cryo-compressed hydrogen is cooled and / or maintained at cry-compressed temperatures using a liquid nitrogen-based refrigeration system, which can advantageously maintain the stored cryo-compressed hydrogen at a temperature which provides a high density at the cryo-compressed hydrogen’s storage pressure. According to various embodiments, the use of both glass-reinforced storage vessels and a liquid-nitrogen-based refrigeration system may synergistically facilitate the cost-effective transportation of cryo- compressed hydrogen at high densities.

[0143] As used herein, the term “cryo” refers to temperatures of 230 K and below.

[0144] As shown in FIG. 2, a ship 1000 includes a hull 1010 and an insulated hold 1020 supported by the hull 1010. A plurality of cryo-compressed hydrogen storage vessels 1030 are disposed in an insulated space 1020a of the hold 1020 and supported by the hull 1010.

[0145] The hold 1020 is cooled by a liquid nitrogen refrigeration system 1040, which keeps a well 1050 at the bottom of the hold 1020 supplied with liquid nitrogen. As shown in FIG. 2, the refrigeration system 1040 includes a nitrogen cooling / liquefaction system 1060, a gaseous nitrogen passageway 1070 for transferring gaseous nitrogen from an insulated space 1020a within the hold 1020 to the liquefaction system 1060, a liquid nitrogen passageway 1080 for transferring liquid nitrogen from the liquefaction system 1060 to the well 1050, and a nitrogen generator 1090 connected to the liquefaction system 1060 or the gaseous nitrogen passageway 1070 for providing make-up nitrogen to the system 1040.

[0146] The cooling / liquefaction system 1060 may comprise any suitable system for cooling and liquifying nitrogen (e.g., boil-off gas liquefaction system). According to various embodiments, the system 1060 comprises a series of compressors and intercoolers.

[0147] The nitrogen generator 1090 may comprise any suitable nitrogen generator. The illustrated generator 1090 extracts nitrogen from ambient air, as is known in the art. According to various embodiments, the nitrogen generator provides isolated nitrogen, which is 90+ %, 91+ %, 92+ %, 93+ %, 94+ %, 95+ %, 96+ %, 97+ %, 98+ %, 99+ %, 99.9+ %, 99.99+ %, and / or 99.999+ % nitrogen to the passageway 1070, liquefaction system 1060, and / or insulated space 1020a.According to various embodiments, the nitrogen generator 1090 comprises a compressor that is configured to compress ambient air from around the ship 100, and a pressure swing absorption device configured to separate nitrogen out of compressed air. According to various embodiments, the use of such high purity nitrogen advantageously reduces an amount of flammable oxygen disposed within the insulated space 1020a, which can help to avoid fires and explosions within the insulated space 1020a of the hold 1020.

[0148] According to various embodiments, an oxygen concentration in the liquid in the well 1050 is low, but may still be higher than a gaseous oxygen concentration in the gaseous portion of the insulated space 1020a of the hold 1020. This could occur, for example, because the boiling point of oxygen is higher than the boiling point of liquid nitrogen, so oxygen in the space 1020a will tend to condense and collect in the well 1050. This process may naturally remove gaseous oxygen from the space 1020a to further reduce a risk of fire within the space 1020a.

[0149] According to various embodiments, an oxygen sensor is disposed in the well 1050 to sense a concentration of oxygen within the liquid nitrogen in the well 1050. If a sensed oxygen level within the liquid in the well 1050 exceeds a predetermined minimum, the liquid in the well 1050 may be purged (e.g., in to the ambient environment), and fresh liquid nitrogen with less oxygen may be generated and pumped into the space 1020a so as to lower an overall concentration of oxygen within the space 1020a.

[0150] According to various alternative embodiments (e.g., where the vcsscl(s) 1030 store inert or non-flammable liquids), the liquid air may be used in place of liquid nitrogen to cool the space 1020a.

[0151] In the embodiment illustrated in FIG. 2, the passageway 1080 delivers liquid nitrogen directly into the well 1050. However, according to alternative embodiments, thepassageway 1080 may alternatively spray liquid nitrogen into the space 1020a from above, which may help to ensure a colder and / or more homogeneous temperature throughout space 1020a.

[0152] According to various embodiments, the nitrogen generator 1090 may be omitted (e.g., if sufficient liquid nitrogen is already available in the well 1050).

[0153] The system 1040 (including the liquefaction system 1060, nitrogen generator 1090, and passageways 1070, 1080) are all mounted to or otherwise supported by the ship 1000. According to various alternative embodiments, the nitrogen generator 1090 may alternatively be separate from the ship 1000, and only intermittently connected to the ship 1000 and system 1040 so as to provide make-up nitrogen as needed (e.g., at a port). In such embodiments, the nitrogen generator 1090 may be a land-based, stationary system.

[0154] The well 1050 is a depression at the bottom of the insulated space 1020a within the hold 1020, and acts to collect and centralize the liquid nitrogen in the space 1020a. The well 1050 reduces sloshing of the liquid nitrogen, and tends to reduce a likelihood that the liquid nitrogen could slosh around so much during wave-induced rocking of the ship 1000 to damage the insulation (e.g., foam) of the insulated hold 1020. According to various embodiments, the floor of the insulated space 1020a may include baffles that further impede sloshing of the nitrogen around in the hold 1020.

[0155] While operating, the system 1040 ensures that a volume of liquid nitrogen remains in the well 1050. The insulated space 1020a is maintained at a pressure near or at atmospheric pressure (e.g., between 0 and 0.1 or 15 psig relative to an ambient pressure outside the ship 1000). According to various embodiments, the pressure within the insulated space 1020 is maintained by the 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 the desired range (e.g., 0-15 or 0 to O.lpsig relative to the ambient pressure around the ship 1000). As a result, as liquid nitrogen in the space 1020a evaporates into gaseous nitrogen, the system 1040 receives the gaseous nitrogen and reliquefies it. That selective reliquification process enables the system 1040 to control a pressure within the space 1020a. Controlling the pressure within the space 1020a also controls the temperature within the space 1020a by controlling the rate of boil-off of the liquid nitrogen in the space 1020a.

[0156] As shown in FIG. 2, according to various embodiments, a vent passageway 1100 extends between the insulated space 1020a and an ambient environment 1120 outside the ship 1000.A pressure-relief valve 1110 in the passageway 1100 is configured to vent gas from the insulated space 1020a to the ambient environment 1120 if a pressure in the insulated space 1020a exceeds a predetermined pressure, e.g., a pressure that is (a) at least 0.001, 0.1, 0.5, 2, and / or 15psig relative to a pressure of the ambient environment 1120 outside the ship 1000, (b) less than 15, 10, 5, 2, 1, and / or O.lpsig and / or (c) at a set point between any two such values (e.g., a predetermined pressure that is between 0.001 and 15 psig). According to various embodiments, the passageway 1100 and valve 1110 may comprise an emergency burst hatch separating the insulated space 1020a from an ambient environment 1120 outside the ship 1000.

[0157] According to various embodiments, the insulated space 1020a is almost entirely filled with gaseous nitrogen, which helps to suppress fires or explosions in the insulated space 1020a by substantially depriving the space 1020a of oxygen.

[0158] Liquid nitrogen in the well 1050 and insulated space 1020a keeps the insulated space 1020a cold. The liquid nitrogen evaporates as needed to keep the space 1020a cold. Liquid nitrogen stored in the well 1050 and insulated space 1020a also acts as a thermal mass buffer, which can temporarily keep the insulated space 1020a cold, even if the system 1040 is turned off or fails. The stored liquid nitrogen in the insulated space 1020a can therefore delay or prevent an emergency situation, which might otherwise occur if the temperature rises within the insulated space 1020a, causing a temperature and / or pressure within the vessels 1030 to approach their rated / permissible maximum temperature and / or pressure.

[0159] According to various embodiments, the insulated hold 1020 and cooling system 1040 maintain the insulated space 1020a and / or an interior space 1030a (see FIG. 5) within the vessels 1030 at a temperature T near the -321 degrees Fahrenheit temperature of atmospheric-pressure liquid nitrogen. According to various embodiments, the temperature T is (a) at least -352, -350, - 330, -325, and / or -320 degrees F, (b) less than or equal to -20, -40, -60, -80, -82, -100, -140, -200, - 240, -280, -310 and / or -315 degrees F, and / or (c) between any two such values (e.g., between -352 and -20 degrees F, between -321 and -280 degrees F, between -321 and -300 degrees Fahrenheit). As shown in FIG. 3, such cryogenic storage temperatures within the insulated space 1020 facilitate high density storage of hydrogen, particularly at the pressures suitable for the vessels 1030.

[0160] According to various embodiments, a pressure of the hydrogen within the vessels 1030 during transportation on the ship 1000 is (1) at least at least 250, 300, 350, 400, 450, 500, 600, 700, 800, 900, 1000, 1500, 2000, 2500, 3000, 3500, 4000, 4500, 5000, 6000, 7000, 8000, 9000,10000, 11000, and / or 12000 psig, (2) at most 14000, 12000, 10000, 8000, 6500, 5000, 4500, 4000, 3500, 3000, 2000, 1500, 1250, and / or 1000 psig, and / or (3) any pressure between any two such values (e.g., between 250 and 14000 psig, between 900 and 10,000 psig, between 1500 and 4500 psig).

[0161] According to various embodiments, a density of the hydrogen within the vessels 1030 is (a) at least 1.0, 1.5, 2.0, 2.5, 3.0, 3.5, 4.0, 4.5, 5.0, 5.5, and / or 6.0 lbm / ft3, (b) less than or equal to 6.0, 5.5, 5.0, 4.5, 4.0, 3.5, 3.0, 2.5, 2.0 and / or 1.5 lbm / ft3, and / or (c) between any two such values (e.g., between 1.0 and 6.0 lbm / ft3, between 1.0 and 5.5 lbm / ft3, between 3.0 and 5.0 lbm / ft3, between 3.5 and 5.0 lbm / ft3).

[0162] The total number and size of the vessels 1030 may depend on the size of the insulated space 1020a and ship 1000. According to various embodiments, the ship’s hold 1020 and its insulated space 1020a may house (a) at least 10, 50, 100, 200, 300, 400, and / or 500 vessels 1030, (b) less than 1000, 900, 800, 700, 600, 500, 400, 300, 200, 100, 50, and / or 10 vessels 1030, or (c) any number between any two such numbers (e.g., between 10 and 1000 vessels 1030, between 50 and 500 vessels). According to various embodiments, a combined total volumetric capacity of the plurality of vessels 1030 in the insulated space 1020 is (a) at least 35, 50, 75, 100, 250, 500, 750, 1,000, 5,000, 10,000, 25,00050,000, 100,000, 200,000, 300,000, 400,000, 500,000, 600,000, 700,000, 800,000, 900,000, and / or 1,000,000 ft3, (b) less than 1,000,000, 750,000, 500,000, 250,000, 100,000, 50,000, 40,000, 30,000, 20,000, 10,000, 5,000, 2500, 1000, 500, 250, 100, 75, and / or 50 ft3, and / or (c) between any two such numbers (e.g., between 35 and 1,000,000 ft3).

[0163] In the illustrated embodiment, the hold 1020 and insulated space 1020a are sized to store numerous vessels 1030. However, according to alternative embodiments, the hold 1020 and space 1020a may be sized to house a single vessel 1030.

[0164] According to various embodiments, the hold 1020 may comprise any suitable thermal insulation (e.g., foam, dead spaces, etc.) to thermally insulate the space 1020a.

[0165] While FIG. 2 illustrates the cryo-compressed hydrogen transportation vehicle as a ship 1000, the vehicle could alternatively be any other suitable vehicle (e.g., a barge, a combination of one or more rail cars, a wheeled vehicle, an ISO container and semi-trailer, etc.) without departing from the scope of the invention. Similarly, while FIG. 2 illustrates the storage container 1020 and storage space 1020a as being defined by a ship’s hold, the container 1020 mayalternatively be any other type of suitable container (e.g., an ISO container, a rail car, etc.) without departing from the scope of the invention.

[0166] Liquid Nitrogen Displacement

[0167] According to various embodiments, liquid nitrogen can be stored within the insulated space 1020a (a) outside of the vessels 1030, (b) within the interior space 1030a of the vessels 1030, and / or (c) both within and outside of the vessels 1030. According to various embodiments, liquid nitrogen is used as a displacer / ballast within the vessels 1030 so as to facilitate substantially isothermal and isobaric transfer of cryo-comprcsscd hydrogen into and out of the vessels 1030.

[0168] According to various embodiments, liquid nitrogen is used as a displacer / ballast in a similar manner as hydraulic fluid is used in WO 2018 / 144328, which is incorporated by reference herein in its entirety.

[0169] As shown in FIG. 4, a liquid nitrogen displacement system 1500 is supported by the ship 1000. The system 1500 includes a liquid nitrogen storage container 1510 that is operatively connected to the interior space 1030a of one or more of the vessels 1030 via a liquid nitrogen passageway 1520 that fluidly connects to a liquid port 1580 leading into the interior space of the vessel 1030. Disposed in parallel within the passageway 1520 is: a pump 1530 for pumping liquid nitrogen from the storage container 1510 to the vessel(s) 1030, an optional pump 1540 for pumping liquid nitrogen from the vessel(s) 1030 to the storage container 1510, and a pressure-regulated valve 1550, which permits liquid nitrogen to flow from the vessel(s) 1030 to the storage container 1510 when a pressure in the vessel(s) 1030 exceeds a predetermined value (e.g., a value at or slightly above a desired vessel 1030 pressure P).

[0170] According to various embodiments, the pumps 1530, 1540 are replaced by a single reversible pump that is disposed in line with (i.e., disposed sequentially along the passageway with) the valve 1550 or parallel to the valve 1550.

[0171] According to various embodiments, the vessels 1030 are at a much higher pressure than the storage container 1510 (e.g., if the container 1510 is kept at a low pressure or at ambient pressure). The pressure difference may tend to cause liquid nitrogen to flow quickly from the vessels 1030 to the container 1510 when flow in that direction is created via use of the pump 1540 (or the reversible pump). According to various embodiments, the pump 1540 (or reversible pump) is used as a kinetic brake to slow, cool down, and control the movement of liquid nitrogen from the high-pressure vessels 1030 back to the lower pressure storage container 1510. The pump 1540 maybe combined with a generator or other mechanical or electrical component that enables recovery of the energy generated by this braking effect when liquid nitrogen is driven by the pressure differential through the pump 1540 (or reversible pump) and into the container 1510.

[0172] According to various embodiments, the storage container 1510 may be supplied with liquid nitrogen from any suitable source (e.g., the nitrogen liquefaction system 1060, the well 1050, etc.).

[0173] According to various embodiments, the liquid nitrogen storage container 1510 may be disposed in the insulated space 1020a. According to various embodiments, the well 1050 may be the storage container 1510 (preferably in embodiments in which hydrogen is effectively isolated from or separated from liquid nitrogen used by the system 1500 when the liquid nitrogen is not in the vessel(s) 1030). Alternatively, the liquid nitrogen storage container 1510 may be supported by the ship 1000, but disposed outside of the insulated space 1020a. The container 1510 may be an insulated container if stored outside of the insulated space 1020a. If the container 1510 is stored in the insulated space 1020a, insulation may be omitted so that the liquid nitrogen in the container 1510 helps to cool the insulated space 1020a.

[0174] Before loading the vessel 1030 with cryo-compressed hydrogen, liquid nitrogen is pumped by the pump 1530 from the storage container 1510 into the interior space 1030a of the vessel 1030 to fill the vessel 1030. To load the vessel 1030, cryo-compressed hydrogen is transferred into the vessel 1030 via a hydrogen passageway 1560 that fluidly connects to a gas port 1570 leading into the interior space 1030a of the vessel 1030. The incoming cryo-compressed hydrogen preferably arrives at the vessel 1030 at approximately the temperature T of the insulated space 1020a and at or near’ the preferred storage pressure P. The pressure-regulated valve 1550 is set to allow nitrogen to flow from the vessel 1030 to the storage container 1510 when the pressure within the vessel 1030 exceeds the pressure P. As a result, liquid nitrogen empties out of the vessel 1030 as cryo-compressed hydrogen loads into the vessel 1030 so that the hydrogen loading process is substantially isothermal and isobaric.

[0175] To transfer cryo-compressed hydrogen out of the vessel 1030, liquid nitrogen is pumped from the storage container 1510 to the interior space 1030a of the vessel 1030 by the pump 1530 at a rate that substantially matches the rate at which cryo-compressed hydrogen leaves the vessel 1030 via the passageway 1560 so that the unloading process is substantially isothermal and isobaric.

[0176] When the vessel 1030 is not being used to store cryo-compressed hydrogen, any liquid nitrogen in the vessel 1030 may be pumped by the pump 1540 from the vessel 1030 to the storage container 1510. This process may leave the unused vessel 1030 at ambient pressure. According to various embodiments, the compressor 1540 is omitted altogether.

[0177] According to various embodiments, when the vessel 1030 is not in use but is filled with liquid nitrogen, gaseous nitrogen may be injected into the vessel 1030 at or around the pressure P so as to displace the liquid nitrogen from the vessel 1030 to the storage container 1510 via the passageway 1520 and valve 1550.

[0178] According to various embodiments, the vessel 1030 is kept at or around pressure P and temperature T during the loading cycle, unloading cycle, and / or when not being used to store cry-compressed hydrogen. By maintaining the vessel 1030 at or around the pressure P and at or around a cryogenic temperature T throughout the vessel 1030’s use, the vessel 1030 experiences reduced pressure cycles, temperature cycles, pressure-based expansion / contraction, and / or temperature-based expansion / contraction, which leads to less fatigue of the vessel 1030 and a longer useful service life for the vessel 1030.

[0179] In the illustrated embodiment, the gas port of the vessel 1030 is at or near the top of the vessel 1030, while the liquid port 1580 is disposed at or near the bottom of the vessel 1030 (as oriented relative to gravity). According to various embodiments, the liquid port opens into the bottom of the interior space 1030a by penetrating a bottom of the vessel 1030. Alternatively, as shown in FIG. 5, the liquid port 1580 may fluidly connect to a bottom of the interior space by penetrating a top of the vessel 1030 and extending via a tube / passageway 1580a to the bottom of the interior space 1030a of the vessel 1030.

[0180] Cryo-compressed hydrogen is lighter than compressed or liquid nitrogen, so cryocompressed hydrogen will tend to float to the top of the vessel 1030 toward the port 1570 while nitrogen will tend to sink to the bottom toward the port 1580. As shown in FIG. 5, according to various embodiments, to further discourage intermixing of hydrogen and nitrogen within the interior space 1030a, a baffle 1600 is disposed in the interior space 1030a. As shown in FIG. 5, the baffle 1600 may comprise one or more horizontal structures within the interior space, which slow down vertical movement of fluids within the interior space. Additionally and / or alternatively, the baffle 1600 may comprise a mesh (e.g., expanded metal sheets) or other suitable structures.

[0181] According to various embodiments, as shown in FIG. 5, a nitrogen / liquid sensor 1610 may be disposed in the port 1570 to sense liquid nitrogen. The sensor 1610 is operatively connected to a sensor-controlled valve 1600 (see FIG. 4) in the passageway 1560. The sensor 1610 closes the valve 1600 when nitrogen / liquid is sensed by the sensor 1610. As a result, the sensor 1610 and valve 1600 prevent nitrogen from flowing through the hydrogen passageway 1560. Similarly, a gas / hydrogen sensor 1620 is disposed in the port 1580 to sense hydrogen / gas. The sensor 1620 is operatively connected to a sensor-controlled valve 1590 (see FIG. 4) in the passageway 1520 and configured to close the valve 1590 when hydrogen is sensed. As a result, the sensor 1620 and valve 1590 can close to prevent hydrogen from escaping from the vessel 1030 through the passageway 1520. The sensors 1610, 1620 may be used to sense when the hydrogen loading and unloading cycles, respectively, have been completed for the associated vessel 1030.

[0182] In addition or alternative to using a baffle 1600, a float structure may be disposed in the interior space 1030a and have a density between that of the cryo-compressed hydrogen in the vessel 1030 and that of liquid nitrogen in the vessel 1030a. The float is vertically movable within the interior space 1030a of the vessel 1030. As a result, the float will tend to float on the liquid nitrogen, and sink below the cryo-compressed hydrogen, which will tend to keep the hydrogen and nitrogen separated. Additionally and / or alternatively, a sensor may be added to sense a location of the float. Such a float sensor could be used in addition to or in the alternative to the above-discussed sensors 1610 and / or 1620 so as to sense when the vessel 1030 is loaded with cryo-compressed hydrogen or unloaded of cryo-compressed hydrogen. The float sensor may be operatively connected to the valves 1590, 1600 to close the valve 1600 when the hydrogen unloading cycle is completed and / or close the valve 1520 when the hydrogen loading cycle is completed.

[0183] Storage Vessels 1030

[0184] According to various embodiments, the vessels 1030 comprise glass-reinforced vessels 1030, which are wrapped in glass (e.g., fiberglass). Reinforcing glass is stronger at the cryogenic temperature T within the insulated space 1020a than glass is at higher temperatures (e.g., 273 K). See 1968 Paper by Rockwell Corporation on Glass Composites. This temperaturedependent property of glass makes it particularly well suited for use in reinforcing the vessels 1030 of the ship 1000. The low cryogenic temperature T within the insulated space 1020a synergistically both (a) reduces the temperature of the hydrogen, which increases the hydrogen’s density and the amount of hydrogen that can be transported on the ship 100, and (b) increases the strength of theglass -reinforced vessels 1030. The cold-temperature strength of the reinforcing glass enables (a) the vessels 1030 to be maintained at a higher pressure (and thus store more hydrogen per ship 1000) and / or (b) the vessels 1030 to use less reinforcement material and thus be less expensive and / or lighter.

[0185] According to various embodiments, as shown in FIG. 5, the vessel 1030 comprises a composite reinforcement 1030b disposed outside of a liner 1030c. According to various embodiments, the composite reinforcement 1030b comprises a mixture of glass (e.g., fiberglass strands) and resin. According to various embodiments, the liner 1030c comprises HDPE (c.g., 8 mm thick), PA-6 nylon (e.g., 0.2 mm thick), UHMWPE (e.g. 8mm thick), or 316L stainless steel (e.g., 0.1 mm thick).

[0186] According to various embodiments, the glass-reinforced vessel 1030 is cooled to the temperature T before being pressurized so as to take advantage of the vessel’s higher glass strength at lower temperatures before pressurizing the vessel 1030.

[0187] As shown in FIG. 4, the gas port 1570 and / or passageway 1560 includes a pressurerelief valve 1650, which may connect to a further vent passageway 1660 so as to vent pressurized gas from within the vessel 1030 to a safe location outside the hold 1020 (e.g., an ambient environment 1120 around the ship 1000). According to various embodiments, the valve 1650 is incorporated into the vessel 1030 itself, or may instead be incorporated into a passageway 1560 that is in fluid communication with the interior space 1030a of the vessel 1030. The relief valve 1650 may be any type of suitable valve (e.g., a pressure -regulated valve, an emergency burst valve / disc, an excess flow valve, etc.) that opens in response to a pressure in the interior space 1030a of the vessel 1030 exceeding a predetermined pressure (e.g., a rated pressure of the vessel 1030).

[0188] According to various embodiments, and as shown in FIG. 6, the vessel 1030 is made by: (1) inserting an expandable mechanical scaffolding 1800 through a hole 1030d (see FIG. 5) in a liner 1030c, (2) radially expanding the scaffolding 1800 within the interior space 1030a inside the liner 1030c so as to form a hoop shape, which mechanically supports the liner 1020b in its proper shape (c.g., a generally cylindrical shape with domed ends) during the manufacturing process, (3) wrapping the scaffolding-supported liner 1020c with a composite layer 1030b including uncured resin, (4) allowing the resin to set, (5) collapsing the scaffolding 1800, (6) removing the collapsed scaffolding 1800 through the hole 1030d from the liner 1030c, and (7) attaching the ports 1570 and / or 1580 to the hole 1030d in the liner 1020c so as to form the interior space 1030a, which issealed except for the ports 1570 and / or 1580. According to various embodiments, the baffle 1600 and / or tube 1580a may be inserted into the interior space 1030a before step (7). Depending on the size of the hole 1030d, the baffle 1600 may be a collapsible baffle 1600 that is collapsed to fit through the hole 1030d and then is expanded within the interior space 1030a (e.g., like how the mast and sails of a ship-in-a-bottle are raised).

[0189] In contrast with bladders that may alternatively be used to support the liner 1030c during wrapping, the scaffolding 1800 is non-inflatable, but instead relies on relative movement between pieces of the scaffolding 1800 to expand and collapse (e.g., 4-bar linkages).

[0190] The scaffolding 1800 can be collapsed sufficiently to fit through the hole 1030d (see FIG. 5), and can then be expanded within the liner 1030c to mechanically support the liner 1030c during the above-discussed steps (3)-(4). For example, according to various embodiments, multiple, axially-spaced rings can be inserted into the hole 1030d while the rings are collapsed, and then expand within the vessel 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 for facilitating expansion, via a pneumatic bladder, via a screw-expansion mechanism like to a gear-expansion corkscrew).

[0191] According to various embodiments, the wrapping step (3) occurs while the liner 1030c is disposed in a substantially vertical orientation (i.e., with the elongated axis 1810 of the liner 1030c and vessel 1030 pointing substantially vertically). According to various embodiments, the wrapping step (3) occurs while the elongated axis 1810 of the liner 1030c is within 20, 15, 10, and / or 5 degrees of vertical. Such vertical wrapping may help prevent the liner 1030c from sagging during wrapping.

[0192] According to various embodiments, the composite layer 1030b is wrapped around the liner 1030c in multiple stages, allowing the resin to cure between stages of wrapping. As a result, an initial cured sub-layer of the composite layer 1030b provides mechanical reinforcement to the liner 1030c during subsequent wrapping with additional composite reinforcement sub-layers. According to various embodiments, the multi-stage wrapping process may avoid any need to use the scaffolding 1800 or other internal reinforcing structures (e.g., an inflatable bladder). According to various embodiments, the composite layer 1030b is wrapped around the liner 1030c in at least 2, 3, and / or 4 stages, with resin curing between each stage. According to various embodiments, the first sub-layer of the composite layer 1030b is thinner and lighter than subsequent sub-layers. In suchembodiments, the strength of the first sub-layer helps to retain the liner 1030c in shape when subsequent, heavier sub-layers of the composite layer 1030b are added.

[0193] According to various embodiments, the composite reinforcement layer 1030b comprises (a) at least 30, 40, 50, and / or 60 weight % fiber glass, (b) less than or equal to 90, 80, 70, and / or 60 weight % fiber glass, and / or (c) between any two such values (e.g., 30-90 weight % fiber glass). 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 wt % resin, (b) less than or equal to 50, 40, 30, 25, 20, 15, and / or 10 weight % resin, and / or (c) between any two such values (e.g., 1-50 weight % resin, 10-20 weight % resin).

[0194] According to various embodiments the composite layer 1030b also comprises (a) at least 1, 2, 3, 4, 5, 6, 7, 8, 9, 10, 15, and / or 20 wt % insulation, (b) less than or equal to 50, 40, 30, 25, 20, 15, and / or 10 weight % insulation, and / or (c) between any two such values (e.g., 1-50 weight % insulation, 10-20 weight % insulation). According to various embodiments the insulation may comprise any suitable insulation (e.g., a fire-retardant insulation such as perlite). According to various embodiments, the composite layer 1030b is fire-retardant (e.g., via a fire retardant compound added into the resin / composite mix such as magnesium oxide, via an additional layer that is non-mechanical and could be made from mineral wool, chopped glass fibers (w / o resin), or perlite if the combination of insulation and fire resistance are desired).

[0195] As shown in FIG. 5, the liner 1030c may comprise one or more expansion joints 1030e. The expansion joint 1030e extends around the circumference of the liner 1030c and allows the liner 1030c to axially expand and contract (up and down as shown in FIG. 5). According to various embodiments, the expansion joint 1030e comprises one or more corrugations, accordionfolds, or other undulations in the liner 1030c. These expansion joints 1030e enable the liner 1030c to axially expand and contract as the temperature and / or pressure in the vessel 1030 changes during use.

[0196] Air Change Control

[0197] As shown in FIG. 7, the insulated storage hold 1020 may have inlet and outlet vents 2000, 2010 and associated inlet and outlet fans 2020, 2030. The vents 2000, 2010 may be louvered vents that automatically open when the fans 2020 or 2030 are on and close when the fans 2020 and 2030 are off. In embodiments in which the hold 1020 is cooled, the vents 2000, 2010 and fans 2020,2030 may be used only when necessary to vent the insulated space 1020a of potentially explosive or otherwise dangerous gases (e.g., hydrogen).

[0198] According to alternative embodiments, including as shown in FIG. 7, the hold 1020 and space 1020a are not cooled and / or not insulated. In such embodiments, the temperature and pressure within the space 1020a may be approximately the same as the ambient environment 1120 outside the ship 1000. In such embodiments, the fans 2020, 2030 may operate continuously so as to continuously ventilate the space 1020a at a desired rate of air changes per hour (ACH).

[0199] As shown in FIG. 7, the gas ports 1570 of each of the vessels 1030 may connect to the common gas passageway 1560 via respective isolation valves 2040 disposed outside of the respective vessels 1030. The valves 2040 may be selectively closed to isolate the fluid stored in each vessel 1030 from the other vessels 1030 and the space 1020a (e.g., in case of a leak in one or more vessels 1030 or associated passageways).

[0200] As shown in FIG. 7, one or more gas sensors (e.g., hydrogen sensors) 2050 may be disposed in the space 1020a to sense the presence of flammable gases (e.g., hydrogen that leaked from the vessel(s) 1030) or other hazardous gases (e.g., if hazardous gases are stored in the vessels 1030).

[0201] As shown in FIG. 7, one or more temperature sensors 2060 may be disposed in the space 1020a to sense the temperature within the space 1020a.

[0202] As shown in FIG. 7, an electronic controller 2070 is operatively connected (e.g., via wired or wireless communications) to the valves 2040, fans 2020, 2030, and sensors 2050, 2060 to control the fans 2020, 2030 and valves 2040 based on sensed parameters from the sensors 2050, 2060.

[0203] According to various embodiments, the controller 2070 may comprise any suitable analog or digital controller (e.g., a personal computer with an A / D in / out capability) configured to receive signals from the sensors 2050, 2060, and send control signals to the fans 2020, 2030 and valves 2040 so as to control the operation and / or flowrate of the fans 2020, 2030, and to close (or open) the valves 2040.

[0204] According to various embodiments in which the space 1020a is kept around ambient temperature (rather than at a cooled / cryo temperature), the controller 2070 controls the fans 2020, 2030 so as to provide a predetermined number of ACH (air changes per hour). The controller 2070 may control the ACH by operating one, a plurality, or all of the fans 2020, 2030 discontinuously ata relatively higher flow rate or continuously at a relatively lower flow rate. According to various embodiments, the controller 2070 may be programmed to increase the ACH in response to the sensed temperature in the space 1020a exceeding a predetermined value(s). According to various embodiments, the controller 2070 is programmed so as to increase the ACH to at least a predetermined value in response to sensing a concentration of leaked gas (e.g., CNG, hydrogen) above a threshold concentration within the space 1020a. According to various embodiments, the controller 2070 is configured to dynamically control the ACH value so as to ensure that the sensed concentration of flammable gas in the space 1020a remains below a lower explosion limit (LEL) concentration. According to various embodiments, the controller 2070 is programmed to close the valves 2040 and isolate the vessels 1030 from each other in response to sensing a flammable gas concentration within the space 1020a above a predetermined value.

[0205] The controller’s ability to keep the space 1020a below the LEL is useful in embodiments in which a vessel 1030’s pressure relief valve 1650 might vent gas from an overpressurized vessel 1030 into the space 1020a (i.e., embodiments in which the pressure relief valve does not vent to the ambient environment 1120).

[0206] According to various embodiments, a temperature sensor 2060 used to sense the temperature in the space 1020a and / or vessels 1030 comprises a thermometer. As shown in FIG. 8, the temperature sensor 2060 may instead comprises a pressure-based temperature sensor 3000. The sensor 3000 comprises sealed tubing 3010 within the space 1020a, a pressure sensor 3020, and fluid 3030 disposed within the tubing 3010. The path of the tubing 3010 may be three dimensional. The tubing 3010 may extend along the perimeter of the space 1020a (e.g., along all 6 sizes or all eight edges of a box-shaped space 1020a (e.g., if the space 1020a is defined by an ISO container 1020). In the illustrated embodiment, the tubing 3010 comprises a network of tubes with joints and intersections fluidly interconnecting different branches of the tubing 3010. Alternatively, the tubing 3010 may comprise a singular tube 3010, which snakes around to different areas within the space 1020a. According to various embodiments, the tubing 3010 comprises thin-walled tubing with an outside diameter of less than 2, 1.5, and / or 1 inch and / or an inner diameter of less than 2, 1.5, and / or 1”. According to various embodiments, the tubing 3010 comprises a material such as copper with a high coefficient of heat transfer. The tubing 3010 is preferably rigid enough to maintain a relatively constant volume within the tubing 3010 such that changes in pressure within the tubing 3010 do not significantly result from changes in the internal volume within the tubing 3010. According tovarious embodiments, the tubing comprises (a) at least 5, 10, 15, 20, 30, 40, 50, 60, 70, 80, 90, and / or 100 linear feet of tubing 3010, (b) less than 10000, 5000, 1000, 500, and / or 100 linear feet of tubing 3010, and / or (c) a combined length of tubing 3010 between any two such values (e.g., 5- 10000 linear feet of tubing).

[0207] The fluid 3030 within the tubing 3010 comprises a fluid whose volume is highly temperature-dependent at the temperature in which the space 1020a is maintained during normal operation of the vehicle 1000 and at the nominal pressure within the tubing 3010.

[0208] The tubing 3010 fluidly connects to the pressure sensor 3020 so that the sensor 3020 senses a pressure of the fluid 3030 within the tubing 3010. The pressure of the fluid 3030 within the sealed tubing 3010 varies with temperature, so the pressure sensed by the sensor 3020 indirectly measures the temperature within the space 1020a. According to various embodiments, the sensor 3020 comprises a proportional pressure sensor 3020. According to various embodiments, the sensor 3020 operatively connects to and controls the pressure-relief valve 1650 so as to open the valve 1650 and vent gas from within the vessel 1030 via the pressure-relief valve 1650 to the ambient environment 1120 (or another suitable location) in response to the sensor 3020 sensing that a pressure (and therefore temperature) within the space 1020a exceeds a predetermined value (e.g., a value which indicates a fire within the space 1020a).

[0209] Instead of a proportional pressure sensor, the sensor 3020 may comprise a burst disc whose bursting increases a pressure within a signal tube operatively connected to the pressuresensor of the valve 1650.

[0210] The fluid 3030 is preferably pressurized relative to a pressure in the space 1020a so that the sensor 3020 can detect a leak in the tubing 3010 (i.e., if the sensed pressure in the tubing 3010 drops toward or to the pressure within the space 1020a).

[0211] According to various embodiments, the pressure sensor 3020 is disposed within the storage space 1020a or disposed outside of the storage space.

[0212] Double- Walled Safety Hose

[0213] As shown in FIGS. 9-10, a flexible double-walled safety hose 4000 may be used to safely transfer compressed hazardous gas (e.g., cryo-compressed hydrogen, CNG, etc.). The doublewalled hose 4000 comprises an inner, high-pressure hose 4010 disposed within an outer, low- pressure hose 4020. The inner hose 4010 defines an inner space 4010a for transferring pressurizedfluid via the safety hose 4000. An outer space 4020a is defined between the outer wall of the inner hose 4010 and an inner wall of the outer hose 4020.

[0214] The inner and outer hoses 4010, 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, 4020 axially concentric and / or longitudinally aligned. According to various embodiments, the spacer(s) 4030 are flexible (e.g., rope, elastomer) or rigid (e.g., metal rods). The spacer(s) 4030 may act in tension (e.g., like the spokes of a bicycle wheel) and / or compression.

[0215] According to various embodiments, the spaccr(s) 4030 comprise axially-spaccd rings. The inner hose passes through the central holes in the rings. An outer diameter of the rings is small enough to fit inside the outer hose 4020. The rings may be fluid-permeable and / or have longitudinal holes such that fluid in the space 4020a can move through / past the rings, thereby avoiding the build up of pressure between adjacent rings. Alternatively, the inner and / or outer diameters of the rings can be selected so that fluid within the space 4020a can pass between the inner hose 4010 and rings and / or between the outer hose 4020 and rings. According to various embodiments, a spacer ring may be a unitary structure with an annular shape (e.g., like a donut or washer). Alternatively, the spacer ring may comprise 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 rings may comprise any suitable material (e.g., foam, an elastomer, plastic, etc.). The rings may provide thermal insulation to better insulate the interior space 4010a from the ambient environment 1120.

[0216] According to various embodiments, the spacers 4030 are attached at spaced intervals to the outside of the inner hose 4010 and / or the inside of the outer hose 4020. Alternatively, axially- spaced spacers 4030 may connect to each other (e.g., via further spaced in the form of tensile string) to help to maintain axial spacing among the spacers 4030 over the axial length of the hose 4000.

[0217] However, the spacers 4030 may be omitted entirely without deviating from the scope of one or more embodiments.

[0218] The double-walled hose 4000 includes connectors 4040 at the axial ends of the hoses 4010, 4020. According to various embodiments, the connectors 4040 may be configured to fluidly connect ends of the inner space 4010a of the high-pressure hose 4010 to further high-pressure passageways (e.g., any of the above-discussed passageways 350, 1560, 1570).

[0219] The connector 4040 may also be configured to fluidly connect the outer space 4020a inside the outer hose 4020 to a further comparable low-pressure outer space within a connected outer hose. Alternatively, the connectors 4040 may fluidly seal the ends of the outer hose 4020 and the outer space 4020a, such that the connector 4040 does not fluidly connect the outer space 4020a to a further low-pressure outer hose 4020.

[0220] The connectors 4040 may be any type of suitable connector for temporarily or permanently fluidly connecting the inner space 4010a of the hose 4010 (or also the outer space 4020a of the hose 4020) to a further fluid passagcway(s). According to various embodiments, the connectors 4040 may comprise threaded connectors, bayonet connectors, quick-disconnect connectors, etc. The connectors 4040 may alternatively be permanent connectors (e.g., welded joints). According to various embodiments, the connectors 4040 include valves 4110 which fluidly connect to the ends, respectively of the inner space 4010a of the hose 4010. The valves 4110 may be closed before disconnecting the connector 4040 so as to prevent gas within the inner space 4010a from leaking into the environment 1120 when the connectors 4040 are disconnected. Conversely, the valves 4110 may be opened after the connectors 4040 are connected to supply and destination passageways so as to permit fluid transfer through the inner space 4010a of the hose 4010.According to various embodiments, the valves 4110 may be operatively connected to the connector 4040 mechanism so as to automatically open in response to the connector 4040 connecting to a further passageway, and automatically close in response to the connector 4040 disconnecting from a further passageway.

[0221] The hose 4000 also includes a vent hose 4050 having a first end 4050a fluidly connected to the outer space 4020a of the outer hose 4020 and a second end 4050b opening into an area in which is it safe to vent flammable gas (e.g., a portion of the environment 1120 spaced away from people and / or flames). As a result, an interior of the hose 4050 proximate to the end 4050a is in fluid communication with and / or defines a portion of the outer space 4020a.

[0222] A pressure-relief valve 4060 is disposed in the hose 4050. The normally-closed pressure-relief valve 4060 is configured to open and vent fluid from within the outer space 4020a out through the end 4050b when a sensed pressure within outer space 4020a exceeds a predetermined pressure (e.g., a pressure that is (a) at least 145, 200, 300, 400, 500, 750, 1,000, 1,500, 2,000, 2,500, 3,000, 3,500, 4,000, 5,000, 6,000, and / or 7,250 psig, (b) less than 7,500, 7,250, 7,000, 6,000, 5,000, 4,000, 3,500, 3,000, 2,500, 2,000, 1,500, 1,250, 1,000, 750, 500, 400, 300, 200,and / or 150 psig, (c) and / or between any two such values (e.g., between 145 and 7,500 psig, between 1,000 and 5,000psig)). According to various embodiments, the valve 4060 may comprise a selfactuating, pres sure- sensitive valve that opens when the sensed pressure in the outer space 4020a exceed the predetermined pressure and closes when the sensed pressure within the outer space 4020a falls below the predetermined pressure. Alternatively, the valve 4060 may comprise a singleuse, normally-closed valve such as a burst disk, which is calibrated to burst / open at the predetermined pressure and remain open until replaced with a new / replacement valve 4060.

[0223] According to various embodiments, the valve 4060 includes a visual and / or audible alarm, which is triggered by the opening of the valve 4060 to indicate to the hose 4000 operator that the valve 4060 opened and is venting fluid out of the end 4050b.

[0224] According to various embodiments, the valve 4060 may additionally and / or alternatively be operatively connected to valves 4110 at the connectors 4040. In such embodiments, opening of the valve 4060 as a result of a sensed leak in the hose 4010 causes the valves 4110 in or near the connectors 4040 to close and thereby stop further transfer of flammable gas into and out of the ends of the hose 4010.

[0225] According to embodiments in which a portion of the hose 4020 is disposed in an area safe for venting, the hose 4050 may be eliminated, and the valve 4060 operatively connected directly to the outer space 4020a within the hose 4020 at a location where venting of hazardous gas is safe.

[0226] The hose 4000 includes a fluid supply passageway 4070 operatively connecting a source 4080 of fluid to the outer space 4020a. As shown, the passageway 4070 connects to the outer space 4020a via the intermediate hose 4050. However, the passageway 4070 may alternatively directly connect to the outer space 4020a within the hose 4020. According to various embodiments, the source 4080 may comprise the ambient environment 1120 such that the fluid in the outer space 4020a is air. Alternatively, the source 4080 may comprise an inert gas such as nitrogen. According to various embodiments, the source 4080 is pressurized and connected to the passageway 4070 via a pressure-regulated valve that opens to allow fluid from the source 4080 to flow into the outer space 4020a when a pressure within the outer space 4020a is below a set pressure for the space 4020a. According to various embodiments, the set pressure for the outer space 4020a is (a) at least 50, 75, 100, 150, 200, 250, 300, 400, 500, 750, 1,000, 1,250, 1,500, 2,000, 2,500, 3,000, 3,500, and / or 4,000 psig, (b) less than 5,000, 4,500, 4,000, 3,500, 3,000, 2,500, 2,000, 1,500, 1,250, 1,000, 750,500, 400, 300, 250, 150, and / or 100 psig, (c) and / or between any two such values (e.g., between 50 and 5,000 psig, between 2,500 and 4,000 psig)). According to various embodiments, the set pressure is lower than the predetermined release pressure of the valve 4060 (e.g., by at least 25, 50, 75, 100, 150, 200, 250, 300, 400, 500, 750, 1,000, 1,100, 1,200, 1,300, 1,400 and / or 1,500 psig) so that the flow of fluid from the source 4080 into the hose 4020 will not cause the valve 4060 to open.

[0227] As shown in FIG. 10, according to one or more embodiments (e.g., embodiments in which a pressure of the source 4080 fluid is below the set pressure for the outer space 4020a), a compressor 4090 is disposed along the passageway 4070. An inlet of the compressor 4090 fluidly connects, via the passageway 4070, to the source 4080 (e.g., air from the ambient environment). An outlet of the compressor 4090 fluidly connects, via the passageway 4070 (or a direct connection), to the outer space 4020a. The compressor 4090 is configured to compress and transfer fluid from the source 4080 into the interior space 4020a of the hose 4020. According to various embodiments, the compressor 4090 may be a pressure-regulated compressor which turns on when the sensed pressure within the outer space 4020a (e.g., as sensed by a pressure sensor in the hose 4020) falls below the set pressure.

[0228] According to various embodiments, a check valve may be disposed in the passageway 4070 to prevent fluid from flowing from the outer space 4020a to the source 4080 via the passageway 4070. In case of a leak in the high pressure hose 4010, the check valve preferably prevents high pressure hazardous gas from back flowing through the passage 4070 into the source 4080.

[0229] According to various embodiments, the hose 4010 is rated for pressures of (a) at least 2,500, 3,000, 3,500, 4,000, 4,500, 5,000, 6,000, 7,000, 8,000, 9,000, and / or 10,000 psig, (b) less than 15,000, 12,500, 10,000, 9,000, 8,000, 7,000, 6,000, 5,000, 4,500, 4,000, 3,500, and / or 3,000 psig, and / or (c) between any two such values (e.g., between 2,500 and 15,000 psig, between 3,000 and 6,000 psig).

[0230] According to various embodiments, the hose 4010 is rated for low and / or cryogenic temperatures (e.g., temperatures of (a) less than or equal to 233, 220, 200, 180, 160, 140, 130, 120, 110, 100, 90, and / or 80 K, (b) at least 40, 50, 60, 70, 80, 90, 100, 150, and / or 200 K, and / or (c) between any two such values (e.g., between 40 and 223K, between 77 and 100K, between 77 and 90 K). According to various embodiments, the hose 4000 is well suited for transferring very cold (e.g., cryogenic) fluids through the inner space 4010a of the hose 4010 because the outer hose 4020and fluid within the outer space 4020a of the outer hose 4020 provide thermal insulation between the inner hose 4010 and the ambient environment 1120 outside the outer hose 4020.

[0231] According to various embodiments, the outer hose 4020 and pressurized portion of the vent hose 4050 are rated for pressures of (a) at least 500, 750, 1,000, 1,250, 1,500, 2,000, 2,500, 3,000, 3,500, 4,000, 5,000, 6,000, and / or 7,000 psig, (b) less than 8,000, 7,000, 6,000, 5,000, 4,500, 4,000, 3,500, 3,000, 2,500, 2,000, 1,500, 1,250, 1,000, 900, 800, 750, 700, and / or 650 psig, and / or (c) between any two such values (e.g., between 500 and 8,000 psig).

[0232] According to various embodiments, a rated flow rate through the outer space 4020a of the outer hose 4020 (and vent hose 4050 is included in an embodiment) is higher than a rated flow rate of the inner hose 4010 such that the outer hose 4020 and outer space 4020a can accommodate the entire flow of gas passing through the inner space 4010a of the inner hose 4010 (e.g., if the hose 4010 is entirely severed such that the entire flow through the hose 4010 leaks into the outer space 4020a of the outer hose 4020) without bursting the outer hose 4020 (and vent hose 4050 if used). According to various embodiments, the predetermined release pressure of the valve 4060 is preferably lower than the rated pressure of the hose 4020 (and hose 4050 if used) so that the valve 4060 opens before the hoses 4020, 4050 burst.

[0233] According to various embodiments, the source 4080, passageway 4070, and compressor 4090 are omitted. In such embodiments, the outer space 4020a may be fluid tight, and either pressurized or non-pressurized or under a slight vacuum. If non-pressurized, the outer space 4020a may be filled with a gas (e.g., air or an inert gas such as nitrogen) and sealed, or may be empty. In various embodiments, a leak of pressurized gas from the inner space 4010a will leak into the outer space 4020a, raising a pressure within the outer space 4020a, which can trigger the gas leak sensor 4100 and / or cause the pressure relief valve 4060 to open and vent flammable gas at a safe location.

[0234] According to various embodiments, if the outer space 4020a is normally kept at a slight vacuum pressure, the hose 4020 is structurally designed to withstand such a vacuum pressure without leaking. The light- vacuum embodiment may rely on a completely scaled space 4020a, which is sealed while under a slight vacuum pressure. Alternatively, a compressor (e.g., like the compressor 4090, but driving gas in the opposite direction) may be used to maintain a slightly negative pressure within the outer space 4020a relative to the surrounding ambient environment. Such a slight vacuum pressure within the space 4020a may help to discourage or prevent any gasthat has leaked from the hose 4010 into the space 3020a from leaking out into the ambient environment. Such a vacuum pressure system is particularly useful at preventing a small-volume leak in the hose 4010 from causing gas to leak into the ambient environment around the hose 4000.

[0235] According to one or more embodiments, one or more gas sensors 4100 are positioned to sense flammable / hazardous gas in the outer space 4020a of the outer hose 4020, and thereby detect a leak in the inner hose 4010. According to various embodiments, the sensor(s) 4100 may be operatively connected to an alarm (e.g., visual and / or audio alarm) such that the alarm warns hose operators if flammable gas above a certain concentration is detected in the outer space 4020a of the hose 4020.

[0236] According to one or more embodiments, the sensor(s) 4100 operatively connect to and control the valve 4060 so as to open the valve 4060 when flammable gas above a certain concentration is detected within the outer space 4020a. Alternatively, the sensor(s) 4100 are not operatively connected to the valve 4060.

[0237] According to one or more embodiments, the sensor(s) 4100 operatively connect to and control valves 4110 so as to close the valves 4110 (and thereby transfer of fluid into and out of the ends of the hose 4010) when flammable gas above a certain concentration is detected in the outer space 4020a (e.g., as would result from a leak in the hose 4010).

[0238] However, according to alternative embodiments, the sensor(s) 4100 are omitted entirely.

[0239] Hereinafter, operation of the hose 4000 is described with reference to FIG. 10. Before using the hose 4000 to transfer pressurized gas through the hose 4010, the outer space 4020a of the outer hose 4020 is pressurized to the set pressure. Before or after pressurizing the outer hose 4020, an upstream connector 4040 is connected to a source of pressurized gas (e.g., hydrogen or natural gas) to be transferred through the inner space 4010a of the inner hose 4010. A downstream connecter 4040 is connected to a destination passageway for the pressurized gas being transferred through the inner hose 4010. One or more valves in the source and / or destination passageways (and / or valves 4110 of the hose 4010) arc opened to transfer pressurized gas from the source to the destination via the inner space 4010a of the hose 4010. If the hose 4010 leaks, gas will leak into the outer space 4020a of the outer hose 4020, which will raise the pressure within the outer space 4020a, causing the valve 4060 to open and vent flammable gas to the safe location at the end 4050bof the vent hose 4050. Opening of the valve 4060 may automatically trigger an alarm and / or close the valves 4110.

[0240] Dual Pressure Gas Transfer Hose System And Method

[0241] As shown in FIG. 11, a dual pressure gas transfer hose system 5000 may be used to transfer low and / or high pressure compressed gas (e.g., cryo-compressed hydrogen, CNG, etc.) to destinations (e.g., vessels 1030, fuel cells 5005).

[0242] According to various embodiments involving the loading of a vessel 1030, this gas transfer may occur while maintaining a high pressure within the vcsscl(s) 1030 (e.g., in connection with hydraulic, liquid nitrogen, and / or gaseous nitrogen ballasting to maintain a high pressure within the vessels 1030, as explained above). The system 5000 comprises a high-pressure passageway 5010 and a low-pressure passageway 5020.

[0243] The high-pressure passageway 5010 has a first inlet 5010a and a first outlet 5010b. The high-pressure passageway 5010 has a pressure rating of (a) at least 3,000, 4,000, 5,000, 6,000, 7,000, 8,000, 9,000, 10,000, 11,000, 12,000, 13,000, 14,000, and / or 15,000 psig, (b) less than 18,000, 17,000, 16,000, 15,000, 14,000, 13,000, 12,000, 11,000, 10,000, 9,000, 8,000, 7,500, 7,000, 6,500, 6,000, 5,500, and / or 5,000 psig, and / or (c) between any two such values (e.g., between 3,000 and 18,000 psig, between 3,000 and 6,000 psig). According to various embodiments, the high- pressure passageway 5010 has an internal diameter of less than 5, 4, 3, 2, and / or 1 inches. The inlet 5010a is configured to be connected to a source 5015 of high pressure gas (e.g., gas at a pressure of (a) at least 2,500, 3,000, 4,000, 5,000, 6,000, 7,000, 8,000, 9,000, 10,000, 11,000, 12,000, 13,000, 14,000, and / or 15,000 psig, (b) less than 20,000, 15,000, 14,000, 13,000, 12,000, 11,000, 10,000, 9,000, 8,000, 7,500, 7,000, 6,500, 6,000, 5,500, and / or 5,000 psig, and / or (c) between any two such values (e.g., between 3,000 and 20,000 psig).

[0244] A pressure-regulated valve 5035 may optionally be disposed in the passageway 5010 and set to open if the upstream pressure in the passageway 5010 (e.g., on an inlet 5010a side of the valve 5035) exceeds a downstream pressure in the passageway 5010 (e.g., at an outlet 5010b side of the valve 5035). The valve 5035 therefore prevents backflow of gas through the valve 5035 to the inlet 5010a. According to various embodiments, the valve 5035 may be replaced with a check valve to serve the same function.

[0245] The low-pressure passageway 5020 has an inlet 5020a and an outlet 5020b. The low- pressure passageway 5020 has a pressure rating that is lower than the pressure rating of the firstpassageway. According to various embodiments a pressure rating of the passageway 5020 is at least 500, 600, 700, 800, 900, 1,000, 2,000, 3,000, 4,000, 5,000, 6,000, and / or 7,000 psig lower than the pressure rating of the high-pressure passageway 5010. According to various embodiments, the pressure rating of the low-pressure passageway 5020 is (a) at least 500, 600, 700, 800, 900, 1,000, 2,000, 3,000, 4,000, 5,000, 6,000, and / or 7,000 psig, (b) less than 8,000, 7,000, 6,000, 5,000, 4,000, 3,000, 2,500, 2,000, 1,500, 1000, and / or 750 psig, and / or (c) between any two such values (e.g., between 500 and 8,000 psig). According to various non-limiting embodiments, the second passageway 5020 has an internal diameter that is at least 2, 3, 4, 5, and / or 6 inches. The inlet 5010a is configured to be connected to a source 5025 of low pressure gas (e.g., gas at a pressure of (a) at least 250, 300, 400, 500, 600, 700, 800, 900, 1,000, 2,000, 3,000, 4,000, 5,000, 6,000, and / or 7,000 psig, (b) less than 8,000, 7,000, 6,000, 5,000, 4,000, 3,000, 2,000, and / or 1,500 psig, and / or (c) between any two such values (e.g., between 250 and 8,000 psig)).

[0246] The outlet 5020b connects to the passageway 5010 via a check valve 5030, a pressure-regulated valve 5040, and / or a second check valve 5050, which may be arranged in series between the outlet 5020b and passageway 5010. The check valves 5030, 5050 prevent fluid from flowing from the high-pressure passageway 5010 into the low pressure passageway 5020, which helps to ensure that the pressure in the low pressure passageway 5020 stays within the pressure rating of the passageway 5020. The pressure-regulated valve 5040 is configured to close when a pressure within the high pressure passageway 5010 exceeds a predetermined pressure (e.g., a pressure that is below the rated pressure of the low pressure passageway 5020). According to various embodiments, either or both of the check valves 5030, 5050 may be omitted, and the valve 5040 used to prevent backflow of high-pressure gas into the low-pressure passageway 5020. According to various embodiments, the pressure-regulated valve 5040 may be omitted, and one or both check valves 5030, 5050 are used to prevent backflow of gas into the passageway 5020.

[0247] A third passageway 5070 extends from the low-pressure passageway 5020 to the high pressure passageway 5010 via a check valve 5080 (or pressure-regulated valve), compressor 5090, and check valve 5100 (or pressure-regulated valve). The check valve 5080, compressor 5090, and check valve 5100 are sequentially disposed in the third passageway 5070 as the third passageway 5070 progresses from the low-pressure passageway 5020 to the high-pressure passageway 5010. The check valves 5080 and 5100 each prevent fluid from flowing from the high pressure passageway 5010 to the low pressure passageway 5020 via the passageway 5070. Thecompressor 5080 is configured to compress gas received from the low-pressure passageway 5020 and deliver a resulting compressed gas to the high-pressure passageway 5010. Portions of the passageway 5070 upstream from the compressor 5080 may have a lower pressure rating (e.g., the same pressure rating as the passageway 5020), and portions of the passageway 5070 downstream from the compressor 5080 may have a relatively higher pressure rating (e.g., the same pressure rating as the passageway 5010).

[0248] According to one or more embodiments, an optional vent passageway 5200 extends from the low-pressure passageway 5020 (cither directly or via the third passageway 5070). A valve 5210 is disposed in the vent passageway 5020 to allow or prevent venting of gas from the passageway 5020 via the vent passageway 5200. A catalytic heater 5220 or other flaring mechanism is disposed at the end of the vent passageway 5200 to bum / flare gas being vented via the passageway 5200 into the ambient environment 1120.

[0249] The inlets 5010a, 5020a and outlets 5010b, 5020b may incorporate connectors 5230 (e.g., threaded connectors, quick-disconnect connectors, bayonet connectors) for connecting the passageways to upstream sources 5015, 5025 of gas and / or downstream destinations for gas (e.g., the passageway 1560 leading to one or more vessels 1030 and / or other destinations or users of high- pressure gas (e.g., fuel cell 5005)).

[0250] According to one or more embodiments, the passageways 5010, 5020 comprise one or more flexible hoses 5010, 5020 extending from the inlets 5010a, 5020a and connectors 5230 at the outlets 5010b, 5020b. The use of such flexible hoses 5010, 5020 may make it easier to connect the hoses’ inlet connectors 5230 to sources of gas 5015, 5025, respectively. However, according to alternative embodiments, the passageways 5010, 5020 are rigid passageways (e.g., rigid pipe). The system 5000 ensures that a pressure in the passageway 5020 does not exceed a rated pressure of the passageway 5020 even if a pressure in the passageway 5010 exceeds a rated pressure of the passageway 5020.

[0251] According to various embodiments, one or both of the passageways 5010, 5020 (or any other passageway discussed herein) may comprise a doublc-wallcd hose, such as the abovediscussed hose 4000.

[0252] Operation of the dual-pressure hose system 5000 is described with reference to FIG. 11. When the system 5000 is used to transfer gas from a high pressure source 5015 of gas, the high pressure source 5015 of gas is connected to the inlet 5010a of the high-pressure passageway 5010.The outlet 5010b is connected to the destination (e.g., vessel 1030 and / or fuel cell 5005). Gas is then transferred to the destination via the passageway 5010.

[0253] Simultaneously with or in the alternative to loading from the high pressure source 5015 via the inlet 5010a, gas can be loaded from a low pressure source 5025 of gas via the passageway 5020. To do so, the inlet 5020a is connected to the source 5025 of low pressure gas and the outlet 5010b is connected to the passageway 1560 leading to the destination (e.g., vessel 1030 and / or fuel cell 5005). If a pressure in the destination (and therefore portion of the high pressure passageway 5010 between the valve 5035 and destination) is below a pressure of the low pressure source 5025 of gas, the valve 5040 will open and gas will be transferred from the low pressure source 5025 to the destination(s) via the passageway 5020 and passageway 5010.

[0254] If, however, the pressure in the destination exceeds a pressure of the low-pressure source 5025, then gas will not naturally flow from the low pressure source 5025 through the check valves 5030 and valve 5040 to the higher pressure destination. In such case, the compressor 5080 may be used to compress gas from the low-pressure source 5025 so as to deliver gas from the low- pressure source 5025 through the passageway 5020, through the passageway 5070, through the passageway 5010, and through the passageway 1560 to the destination. A refrigeration system may be added to any of the passageways 5070, 5010, 5020 to cool gas being transferred therethrough (e.g., to account for temperature rises caused by compression through the compressor 5080).

[0255] If excess gas is provided by the low-pressure source 5025 (e.g., a well-head which produced unwanted or excess natural gas), the valve 5210 may be opened and excess gas flared via the catalytic heater 5220.

[0256] The above-discussed dual-pressure hose system 5000 is configured to load the vessel(s) 1030 or provide compressed gas to a destination 5005. However, according to various alternative embodiments, for example as illustrated in FIG. 12, a dual-pressure hose system 6000 is additionally and / or alternatively configured to unload compressed gas from the vessel(s) 1030 and / or location 5005. The system 6000 is generally similar to the system 5000, except as explained below. As shown in FIG. 12, the valves 5030, 5040, 5050 of the system 5000 arc replaced with valve 6010, buffer tank 6020, and valve 6030, which are sequentially disposed along a passageway extending between the low-pressure passageway 5020 (e.g., the connector 5230) and the high pressure passageway 5010 and act together to ensure that high pressure gas from the hose 5010 never overpressures the low pressure hose 5020. As shown in FIG. 12, the valve 6010 is a pressure-regulated valve that senses the pressure in the low pressure hose 5020 so as to automatically close the valve 6010 if a sensed pressure in the low pressure hose 5020 exceeds a predetermined value (e.g., 60, 70, 80, 90, and / or 100 % of a rated pressure for the low pressure hose 5020) and automatically opens the valve 6010 if the sensed pressure in the low pressure hose 5020 falls below a predetermined value (e.g., the same value as used to close the valve 6010, or a lower value (e.g., 50, 60, 70, 80, 90, and / or 95% of a rated pressure for the low pressure hose 5020)). The buffer tank 6020 accumulates compressed gas when the valve 6010 is closed so as to prevent over pressuring the passageway between the valves 6010, 6030 if the valve 6010 is abruptly closed. The valve 6030 is a pressure-regulated valve, which is configured to open when a pressure in the passageway connecting the valves 6010, 6030 falls below a predetermined pressure (e.g., 60, 70, 80, 90, and / or 100 % of a rated pressure for the low pressure hose 5020), and close when the pressure in the passageway between the valves 6010, 6030 rises above a predetermined pressure (e.g., the same value as used to close the valve 6030, or a lower value (e.g., 50, 60, 70, 80, 90, and / or 95% of a rated pressure for the low pressure hose 5020)).

[0257] Hereinafter, operation of the dual-pressure hose system 6000 is described with reference to FIG. 12. The system 6000’ s operation to load the vessel(s) 1030 or destination 5005 is generally similar to the loading process for the system 5000, as explained above. However, the system 6000 may also be used to unload compressed gas to a low pressure destination (which replaces or is the same as the source 5025) connected to the low pressure hose 5020 via the connector 5230. The operator opens the valve 6010, which allows higher pressure gas from the vessel 1030, destination 5005, and / or high pressure gas source 5015 to flow from the high pressure hose 5010 sequentially through the 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 the valve 6010, which increases pressure in the buffer 6020 and closes the valve 6030, while relying on the buffer tank 6020 to prevent over pressurization when the valve 6010 is closed but before the valve 6030 has completely closed.

[0258] System For Using Cryo- Compressed Hydrogen At An Oxygen Consuming Apparatus

[0259] FIG. 15 illustrates a system 7500, in which cryo-compressed hydrogen is used at an oxygen-consuming apparatus 7510 (e.g., steel mill, other apparatus with an oxygen-consuming process). A passageway 7520 extends from a source 7530 (e.g., a ship 1000, rail car, barge, system100, system 7000, etc.) of cryo-compressed hydrogen through a heat exchanger 7540, through an expander 7550, and to the apparatus 7510. The system 7500 also includes a refrigeration system 7600 for drawing heat from an air separation unit 7610.

[0260] As shown in FIG. 15, cryo-compressed hydrogen arrives from the source 7530 (e.g., at a temperature of around -320 degrees F), leaves the heat exchanger 7540 at a temperature of around 100 degrees F, leaves the expander at a pressure of less than 10 bars, and is delivered to the apparatus 7510 for use.

[0261] The refrigeration system 7600 comprises a coolant loop / passageway 7620 through which coolant (e.g., nitrogen) circulates between the heat exchanger 7540 and a heat exchanger 7630 of the ASU 7610. According to various embodiments, the heat exchanger 7540 uses the cryo- compressed hydrogen in the passageway 7520 to cool the coolant in the loop 7620 to a temperature of around -310 degrees F. According to various embodiments, the heat exchanger 7630 then uses the cooled coolant in the loop 7620 to absorb heat from the ASU 7610 such that the coolant leaves the heat exchanger 7630 at a temperature of around 90 degrees F. A pump or compressor may be disposed in the loop 7620 to drive circulation of the coolant.

[0262] According to alternative embodiments, excess nitrogen generated by the ASU 7610 is released into the atmosphere or supplied via a passageway from the ASU 7610 to the source 7530 (e.g., to replenish a nitrogen supply of the source 7530). For example, in an embodiment in which the source 7530 is the above-described ship 1000, nitrogen from the ASU 7610 may be used to replenish a nitrogen supply of the ship 1000 (e.g., by replenishing the liquid nitrogen container 1510).

[0263] The ASU 7610 generates gaseous oxygen (O2) 7640, which flows from the ASU 7610 to the apparatus 7510 via a passageway 7650 and is then used by the apparatus 7510.

[0264] As shown in FIG. 15, energy generated by the turbo-expander 7550 is recovered and transferred to the ASU 7610, and used by the ASU 7610 to power the ASU 7610. For example, an electric generator attached to the turbo-expander’s output shaft may generate electricity, which is then transferred to the ASU 7610 via an electrical conduit 7660 and used by the ASU 7610.Alternatively, the output shaft of the turbo-expander 7550 may be mechanically coupled to an input shaft of the ASU 7610 to mechanically drive (either directly or via a gearbox or transmission) one or more components of the ASU 7610 (e.g., a compressor or pump).

[0265] The system 7500 thus takes advantage of the cold temperature and high compression of the cryo-compressed hydrogen to efficiently cool and / or provide power to the ASU 7610, while simultaneously providing to the apparatus 7510 hydrogen that is at a temperature (higher) and / or pressure (lower) that is more useful to the apparatus 7510 than the cryo-compressed temperature and pressure of the hydrogen provided by the source 7530. Also, the expander 7550 operates most efficiently at higher inlet temperatures (more energy in the incoming gas with both high temperature and high pressure) to supply more energy (e.g., electricity via the conduit 7660) to the ASU 7610.

[0266] System For Generating Cryo-Compressed Hydrogen

[0267] FIG. 16 illustrates a system 8000 for generating cryo-compressed hydrogen. The system 8000 comprises a hydrogen source 8010 which provides hydrogen via a passageway 8020 to a hydrogen-consuming apparatus 8030 (e.g., a steel furnace, the apparatus 7510), which may use the hydrogen as an oxide reduction agent. Excess hydrogen flows from the source 8010 to a cryo- compressed hydrogen generator 8040 via a passageway 8050. The generator 8040 then delivers cryo-compressed hydrogen to a destination 8060 via a passageway 8070. An air separation unit 8080 (which may be the above-discussed air separation unit 7610) separates air into gaseous oxygen and liquid nitrogen (as well as smaller quantities of other gases in air). The air separation unit 8080 then provides separated gaseous oxygen to the steel furnace via a passageway 8090. The air separation unit 8080 provides separated nitrogen (e.g., liquid nitrogen) to the generator 8040 via a passageway 8100. The generator 8040 uses the nitrogen preprocessing and / or cooling in connection with its cryo-compression of hydrogen.

[0268] The hydrogen source 8010 may comprise a hydrogen generator 8010. The hydrogen generator 8010 may generate hydrogen via hydrolysis using electricity, and / or by any other method for generating hydrogen.

[0269] The destination 8060 may comprise a cryo-compressed hydrogen vessel (e.g., vessel 1030), which can be mounted on a ship (e.g., ship 1120), rail car, or other vehicle.

[0270] Unless otherwise specifically stated herein, all stated pressures are gauge pressures, rather than absolute pressures.

[0271] The foregoing illustrated embodiments are provided to illustrate the structural and functional principles of various embodiments and are not intended to be limiting. To the contrary, the principles of the present invention are intended to encompass any and all changes, alterationsand / or substitutions thereof (e.g., any alterations within the spirit and scope of the following claims).

Claims

What is claimed is:1 . A method of cooling a compressed gas, the method comprising: splitting a first stream of compressed gas into second and third streams; expansion cooling the third stream; and downstream from where the third stream is expansion cooled, passing the third stream and second stream through a heat exchanger, which transfers heat from the second stream to the third stream.

2. The method of claim 1, wherein: the heat exchanger comprises a first heat exchanger, and the method further comprises, downstream from where the third stream exits the first heat exchanger, passing the third stream and first stream through a second heat exchanger, which transfers 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 exits the second heat exchanger.

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

5. The method of claim 1, wherein said expansion cooling comprises passing the third stream through a turbo expander.

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

7. The method of claim 1, further comprising: compressing the third stream downstream from the heat exchanger to form a fourth stream; and combining the fourth stream and a fifth stream to form the first stream.

8. A system for cooling a compressed gas, the system comprising: a compressed gas inlet for receiving compressed gas; a heat exchanger; a splitter; an expansion cooler; a compressed gas outlet; a first passageway extending from the inlet to the splitter;a second passageway extending sequentially from the splitter, through the heat exchanger, and to the compressed gas outlet; and a third passageway extending sequentially from the splitter, through the expansion cooler, and through the heat exchanger.

9. The system of claim 8, further comprising a refrigeration unit disposed in the first passageway.

10. The system of claim 8, wherein: the heat exchanger comprises a first heat exchanger; the system further comprises a second heat exchanger; the first passageway passes through the second heat exchanger; and the third passageway passes sequentially from the splitter, through the expansion cooler, through first heat exchanger, and then through the second heat exchanger.

11. A combination for transporting cryo-compressed hydrogen, the combination comprising: a vehicle; an insulated space supported by the vehicle; a glass-reinforced storage vessel disposed in the insulated space, the storage vessel defining an interior space; and cryo-compressed hydrogen stored within the vessel, wherein a pressure within the vessel is between 900 and 10,000 psig and a temperature within the vessel is between 60 and 210 K.

12. The combination of claim 11, wherein a density of the cryo-compressed hydrogen within the vessel is at least 2.0 lbm / ft3.

13. The combination of claim 12, wherein the cryo-compressed hydrogen occupies at least 75% of a volume of the vessel.

14. The combination of claim 11, wherein the vehicle comprises a ship.

15. The combination of claim 11, further comprising a pressure relief valve operatively connected to the vessel and configured to vent gas from within the vessel to an ambient environment outside the vehicle if the pressure exceeds a predetermined pressure.

16. The combination of claim 15, wherein the pressure relief valve comprises an emergency burst disc.

17. The combination of claim 11, further comprising a pressure relief valve operatively connected to the insulated space and configured to vent gas from within the insulated space to an ambient environment outside the vehicle if a pressure within the insulated space exceeds a predetermined pressure.

18. The combination of claim 17, wherein the predetermined pressure is between 0.1 and 3.0 psi relative to a pressure of the ambient environment.

19. The combination of claim 15, wherein the pressure relief valve comprises an emergency burst hatch.

20. The combination of claim 11, wherein the vessel comprises a composite reinforced material.

21. The combination of claim 11, wherein the vessel comprises glass that is stronger at the temperature than at 273 K.

22. The combination of claim 11, wherein the vessel comprises a storage cylinder with a liner, wherein the liner comprises HDPE, PA-6, or 316L stainless steel.

23. The combination of claim 11, further comprising an excess flow valve operatively connected to the vessel.

24. The combination of claim 11, wherein the vehicle is a ship.

25. A combination for transporting cryo-compressed hydrogen, the combination comprising: a vehicle; an insulated space supported by the vehicle; liquid nitrogen disposed in the insulated space; a storage vessel disposed in the insulated space, the storage vessel defining an interior space; and cryo-compressed hydrogen stored within the vessel, wherein a pressure within the vessel is between 900 and 10,000 psig and a temperature within the vessel is between 60 and 210 K.

26. The combination of claim 25, wherein the liquid nitrogen disposed in the insulated space is disposed outside the vessel.

27. The combination of claim 26, further comprising:a nitrogen liquefaction system supported by the vehicle and configured to liquify gaseous nitrogen; a liquid nitrogen passageway operatively connecting the liquefaction system to the insulated space and configured to transfer liquid nitrogen from the liquefaction system to the insulated space; and a nitrogen return passageway operatively connecting the insulated space to the liquefaction system and configured to transfer gaseous nitrogen from the insulated space to the liquefaction system so that the liquefaction system can liquify gaseous nitrogen received from the insulated space via the nitrogen return passageway.

28. The combination of claim 27, wherein the liquefaction system is configured to maintain a pressure within the insulated space of 0.1 to 2.0 psig relative to an ambient pressure outside the vehicle.

29. The combination of claim 26, wherein the insulated space comprises a depression shaped and configured to collect and retain liquid nitrogen.

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

31. The combination of claim 30, wherein the nitrogen generator comprises a compressor that is configured to compress ambient air, and a pressure swing absorption device configured to separate nitrogen out of compressed air.

32. The combination of claim 25, wherein the storage vessel comprises a glass- reinforced storage vessel.

33. The combination of claim 25, wherein the liquid nitrogen disposed in the insulated space is disposed in the interior space.

34. The combination of claim 33, wherein the vessel includes a gas port that fluidly connects to an upper portion of the interior space, and a liquid port that fluidly connects to a lower portion of the interior space.

35. The combination of claim 33, further comprising a baffle disposed within the vessel.

36. The combination of claim 33, further comprising a float in the interior space, the float being vertically movable within the interior space, the float separating the interior space intoan upper portion above the float and a lower portion below the float, the float having a density higher than the cryo-compressed hydrogen and lower than the liquid nitrogen.

37. The combination of claim 25, further comprising: a liquid nitrogen storage container; a liquid nitrogen supply passageway connecting the container to the vessel; and a pump positioned and configured to pump liquid nitrogen from the container into the interior space.

38. The combination of claim 37, wherein the pump is configured to pump liquid nitrogen into the interior space during unloading of the cryo-compressed hydrogen from the vessel so as to displace cryo-compressed hydrogen within the interior space and facilitate substantially isothermal and isobaric unloading of the cryo-compressed hydrogen from the vessel.

39. The combination of claim 37, further comprising: a liquid nitrogen return passageway connecting the liquid nitrogen storage container to the interior space; and a valve disposed in the liquid nitrogen return passageway, the valve having an open state in which liquid nitrogen can flow from the interior space to the container, the valve having a closed state preventing liquid nitrogen from flowing from the interior space to the container.

40. The combination of claim 39, wherein the valve comprises a pressure-regulated valve configured to open when a pressure in the vessel exceeds a predetermined pressure.

41. The combination of claim 40, wherein the valve is configured to facilitate substantially isobaric loading of the vessel with cryo-compressed hydrogen.

42. A method of transporting cryo-compressed hydrogen using a vehicle with an insulated space and a storage vessel disposed within the insulated space, the storage vessel defining an interior space, the method comprising: cooling a temperature within the interior space to between 77 and 90 K; pressurizing the interior space to a pressure of between 900 and 10,000 psig; and while the temperature is between 60 and 210 K and the pressure is between 900 and 10,000 psig, transferring cryo-compressed hydrogen into the interior space.

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

44. The method of claim 42, wherein said cooling comprises disposing liquid nitrogen in the insulated space outside of the vessel while the pressure within the interior space is less than 300 psig.

45. A method of making a storage vessel for storing compressed fluids, the method comprising: inserting an expandable scaffolding through a hole in a liner; radially expanding the scaffolding within an interior space inside the liner so as to mechanically support the liner; wrapping a composite reinforcement around the liner while the scaffolding is disposed within the liner, wherein the composite reinforcement comprising glass and resin; curing the resin; collapsing the scaffolding; and removing the mechanical support from the liner via the hole in the liner.

46. The method of claim 45, wherein the liner comprising HDPE, PA-6, or 316L stainless steel.

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

48. The method of claim 47, wherein the composite reinforcement comprises at least 10% insulation.

49. The method of claim 48, wherein the insulation comprises perlite.

50. The method of claim 48, wherein the composite reinforcement comprises a fire retardant.

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

52. The method of claim 51, wherein the expansion joint comprises corrugations in the liner, said corrugations facilitating expansion and contraction of the liner.

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

54. The method of claim 45, wherein the vessel comprises a cylinder that is elongated in an axial direction of the cylinder, and wherein the wrapping occurs while the axial direction is within 10 degrees of a vertical orientation.

55. The method of claim 45, wherein said wrapping comprises: wrapping the liner with a first sub-layer of glass stiffening material and a first sub-layer of resin; curing the first sub-layer of resin; and wrapping a second sub-layer of glass stiffening material and a second sub-layer of resin over top of the first sub-layer of glass stiffening material and first sub-layer of resin.

56. A combination for transporting compressed flammable gas, the combination comprising: a vehicle; an storage space supported by the vehicle; a gas storage vessel disposed within the storage space and defining an interior space, the storage vessel having a pressure relief valve configured to release gas from the within the interior space into the insulated storage space if a pressure within the interior space exceeds a predetermined pressure; a compressed gas stored in the interior space of the storage vessel; a gas sensor disposed within the storage space and configured to detect when a concentration of the gas within the storage space outside of the storage vessel exceeds a predetermined concentration; at least one fan connected to the storage space and configured to exchange air between the storage space and an ambient 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 a rate of air exchange between the storage space and ambient environment in response to sensing that the gas within the storage hold outside of the storage vessel exceeds the predetermined concentration.

57. The combination of claim 56, further comprising a plurality of additional gas storage vessels disposed within the storage space, each of the plurality of additional gas storage vessels having an interior space and a pressure relief valve configured to release gas from within the respective one of the plurality of additional gas storage vessels into the storage space if a pressure within the interior space of the respective storage vessel exceeds a predetermined pressure.

58. The combination of claim 57, wherein the interior space of each of the plurality of storage vessels is fluidly isolated from each other.

59. The combination of claim 56, wherein the at least one fan comprises at least one inflow fan positioned to blow ambient air from the ambient environment into the insulated storage hold, and at least one exhaust fan positioned to blow air from within the insulated storage hold to the ambient environment.

60. A combination for transporting compressed flammable gas, the combination comprising: a container defining a storage space; a comprcsscd-gas storage vessel disposed within the storage space; a pressure-relief valve connected to the vessel so as to vent pressurized gas stored within the vessel when the valve is opened; and a temperature sensor attached to the container, the temperature sensor comprising: at least 10 linear feet of sealed tubing disposed within the storage space; fluid disposed within the tubing; and a pressure sensor attached to the tubing to sense when a pressure of the fluid within the tubing exceeds a predetermined pressure, wherein the pressure sensor is operatively connected to the valve so that the valve opens in response to a pressure sensed by the pressure sensor exceeding the predetermined pressure.

61. The combination of claim 60, wherein the pressure sensor comprises a burst disc.

62. The combination of claim 60, wherein the container comprises an ISO container.

63. A double-walled safety hose comprising: an outer hose; an inner hose disposed inside the outer hose, the inner hose being configured to transfer a pressurized fluid through an inner space of the inner hose from a first end of the inner hose to a second end of the inner hose; an outer space defined between the inner and outer hoses; and a pressure relief valve operatively connected to the outer space and configured to vent fluid from the outer space if a pressure in the outer space exceeds a predetermined pressure.

64. The double-walled safety hose of claim 63, further comprising a vent passageway having first and second ends, a first end of the vent passageway being in fluid communication with the outer space, the pressure relieve valve being disposed in the vent passageway.

65. The double-walled safety hose of claim 63, further comprising a compressor with an outlet fluidly connected to the outer space and configured to transfer compressed fluid into the outer space.

66. The double-walled safety hose of claim 65, wherein the compressor comprises a pressure-regulated compressor configured to sense a pressure in the outer space, and transfer compressed fluid into the outer space when a sensed pressure in the outer space falls below a set pressure.

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

68. The double-walled safety hose of claim 63, wherein the pressure relief valve comprises a single-use burst disk.

69. The double-walled safety hose of claim 63, further comprising a gas sensor positioned to sense the presence in the outer space of a gas that is being transferred through the inner space.

70. A system for transferring compressed gas, the system comprising: a first passageway having a first inlet and a first outlet, the first passageway having a first pressure rating and an internal diameter of less than 2 inches; and a second passageway having a second inlet and a second outlet, the second outlet being connected to the first passageway via a flow control mechanism that prevents fluid flow from the first passageway into the second passageway, the second passageway having a second pressure rating that is lower than the first pressure rating, the second passageway having an internal diameter of over 2 inches, wherein the flow control mechanism comprises a check valve or a pres sure -regulated valve.

71. The system of claim 70, wherein the flow control mechanism comprises a pressure- regulated valve disposed between second outlet and the first passageway, the pressure-regulated valve being configured to close when a pressure within the first passageway exceeds a predetermined pressure.

72. The system of claim 71, further comprising a check valve separating the pressure- regulated valve from the first passageway.

73. The system of claim 72, further comprising an additional check valve disposed between the pressure-regulated valve and second outlet, the additional check valve preventing fluid flow from the from the pressure -regulated valve to the second passageway.

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

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

76. A method for providing hydrogen to an oxygen-consuming apparatus, the method comprising: delivering hydrogen from a source to the oxygen-consuming apparatus via a passageway; transferring heat from an air separation unit to the hydrogen in the passageway; expanding the hydrogen in the passageway; and using the expanding to generate electricity that is then used to power the air separation unit.

77. The method of claim 75, further comprising separating oxygen from air via the air separation unit, and delivering the separated air to the oxygen-consuming apparatus.

78. The method of claim 75, wherein the source comprises a source of cryo-compressed hydrogen.

79. A method for generating cryo-compressed hydrogen, the method comprising: receiving at a cryo-compressed hydrogen generator hydrogen from a hydrogen source; receiving at the cryo-compressed hydrogen generator liquid nitrogen from an air separation unit; cryo-compressing the received hydrogen in the cryo-compressed hydrogen generator using the received liquid nitrogen.

80. The method of claim 79, further comprising: transferring oxygen from the air separation unit to an oxygen-consuming apparatus for use by the oxygen-consuming apparatus; andtransferring hydrogen from the hydrogen source to the oxygen-consuming apparatus for use by the oxygen-consuming apparatus.

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