WO2022171390A1 - Dispositif et procédé de liquéfaction d'un fluide tel que l'hydrogène et/ou de l'hélium - Google Patents
Dispositif et procédé de liquéfaction d'un fluide tel que l'hydrogène et/ou de l'hélium Download PDFInfo
- Publication number
- WO2022171390A1 WO2022171390A1 PCT/EP2022/050973 EP2022050973W WO2022171390A1 WO 2022171390 A1 WO2022171390 A1 WO 2022171390A1 EP 2022050973 W EP2022050973 W EP 2022050973W WO 2022171390 A1 WO2022171390 A1 WO 2022171390A1
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- Prior art keywords
- compression
- cycle gas
- turbines
- turbine
- cycle
- Prior art date
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- 239000012530 fluid Substances 0.000 title claims abstract description 36
- 239000001307 helium Substances 0.000 title claims abstract description 20
- 229910052734 helium Inorganic materials 0.000 title claims abstract description 20
- SWQJXJOGLNCZEY-UHFFFAOYSA-N helium atom Chemical compound [He] SWQJXJOGLNCZEY-UHFFFAOYSA-N 0.000 title claims abstract description 20
- 239000001257 hydrogen Substances 0.000 title claims description 28
- 229910052739 hydrogen Inorganic materials 0.000 title claims description 28
- UFHFLCQGNIYNRP-UHFFFAOYSA-N Hydrogen Chemical compound [H][H] UFHFLCQGNIYNRP-UHFFFAOYSA-N 0.000 title claims description 24
- 238000000034 method Methods 0.000 title claims description 13
- 230000006835 compression Effects 0.000 claims abstract description 169
- 238000007906 compression Methods 0.000 claims abstract description 169
- 239000007789 gas Substances 0.000 claims abstract description 103
- 238000001816 cooling Methods 0.000 claims abstract description 60
- 230000007246 mechanism Effects 0.000 claims abstract description 37
- 238000003303 reheating Methods 0.000 claims abstract description 3
- 238000011144 upstream manufacturing Methods 0.000 claims description 19
- 238000010438 heat treatment Methods 0.000 claims description 9
- 230000008569 process Effects 0.000 claims description 9
- 239000013529 heat transfer fluid Substances 0.000 claims description 7
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 claims description 6
- 150000002431 hydrogen Chemical class 0.000 claims description 6
- 230000008878 coupling Effects 0.000 claims description 5
- 238000010168 coupling process Methods 0.000 claims description 5
- 238000005859 coupling reaction Methods 0.000 claims description 5
- 239000000203 mixture Substances 0.000 claims description 5
- 239000007788 liquid Substances 0.000 claims description 4
- 239000003507 refrigerant Substances 0.000 claims description 4
- 238000005057 refrigeration Methods 0.000 claims description 4
- 238000012546 transfer Methods 0.000 claims description 4
- 229910052757 nitrogen Inorganic materials 0.000 claims description 3
- 238000009826 distribution Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 3
- 239000000243 solution Substances 0.000 description 3
- 230000008901 benefit Effects 0.000 description 2
- 239000002826 coolant Substances 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 238000007710 freezing Methods 0.000 description 2
- 230000008014 freezing Effects 0.000 description 2
- 238000012423 maintenance Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 238000006555 catalytic reaction Methods 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 230000008030 elimination Effects 0.000 description 1
- 238000003379 elimination reaction Methods 0.000 description 1
- 238000000605 extraction Methods 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 238000002955 isolation Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 238000002407 reforming Methods 0.000 description 1
- 238000005070 sampling Methods 0.000 description 1
- 238000004513 sizing Methods 0.000 description 1
- 238000003860 storage Methods 0.000 description 1
- 238000009834 vaporization Methods 0.000 description 1
- 230000008016 vaporization Effects 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
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- F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
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- F25J1/0002—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the fluid to be liquefied
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- F25J1/0007—Helium
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- F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
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- F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
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- F25J1/0052—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using an "external" refrigerant stream in a closed vapor compression cycle by vaporising a liquid refrigerant stream
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- F25J1/0214—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process using a multi-component refrigerant [MCR] fluid in a closed vapor compression cycle as a dual level refrigeration cascade with at least one MCR cycle
- F25J1/0215—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process using a multi-component refrigerant [MCR] fluid in a closed vapor compression cycle as a dual level refrigeration cascade with at least one MCR cycle with one SCR cycle
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- F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
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- F25J1/0243—Start-up or control of the process; Details of the apparatus used; Details of the refrigerant compression system used
- F25J1/0257—Construction and layout of liquefaction equipments, e.g. valves, machines
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- F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
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- F25J1/0284—Electrical motor as the prime mechanical driver
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- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
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- F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
- F25J2230/00—Processes or apparatus involving steps for increasing the pressure of gaseous process streams
- F25J2230/20—Integrated compressor and process expander; Gear box arrangement; Multiple compressors on a common shaft
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
- F25J2230/00—Processes or apparatus involving steps for increasing the pressure of gaseous process streams
- F25J2230/22—Compressor driver arrangement, e.g. power supply by motor, gas or steam turbine
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
- F25J2230/00—Processes or apparatus involving steps for increasing the pressure of gaseous process streams
- F25J2230/42—Processes or apparatus involving steps for increasing the pressure of gaseous process streams the fluid being nitrogen
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
- F25J2240/00—Processes or apparatus involving steps for expanding of process streams
- F25J2240/02—Expansion of a process fluid in a work-extracting turbine (i.e. isentropic expansion), e.g. of the feed stream
- F25J2240/04—Multiple expansion turbines in parallel
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
- F25J2270/00—Refrigeration techniques used
- F25J2270/14—External refrigeration with work-producing gas expansion loop
- F25J2270/16—External refrigeration with work-producing gas expansion loop with mutliple gas expansion loops of the same refrigerant
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
- F25J2290/00—Other details not covered by groups F25J2200/00 - F25J2280/00
- F25J2290/34—Details about subcooling of liquids
Definitions
- the invention relates to a device and a method for liquefying a fluid such as hydrogen and/or helium.
- the invention relates more particularly to a device for liquefying a fluid such as hydrogen and/or helium comprising a fluid circuit to be cooled having an upstream end intended to be connected to a source of gaseous fluid and a downstream end intended to be connected to a member for collecting the liquefied fluid, the device comprising a set of heat exchanger(s) in heat exchange with the fluid circuit to be cooled, the device comprising at least a first cooling system in heat exchange with at least part of the set of heat exchangers, the first cooling system being a refrigerator with a refrigeration cycle of a cycle gas mainly comprising helium, said refrigerator comprising, arranged in series in a cycle circuit: a mechanism for compressing the cycle gas, at least one member for cooling the cycle gas, a mechanism for expanding the cycle gas and at least one member reheating of the expanded cycle gas, in which the compression mechanism comprises at least four compression stages in series composed of a set of compressor(s) of the centrifugal type, the compression stages being mounted on shafts driven in
- the hydrogen (H2) liquefaction solutions of the prior art incorporate cycle compressors which achieve relatively low isothermal efficiencies (of the order of 60% to 65%) and with a relatively limited volume capacity at the cost, however, of a fairly substantial investment and high maintenance costs.
- An object of the present invention is to overcome all or part of the drawbacks of the prior art noted above.
- the device according to the invention is essentially characterized in that the at least one member for cooling the cycle gas is configured to cool the cycle gas at the outlet of at least one of the turbines and in which at least one of the turbines is coupled to the same shaft as at least one compression stage so as to provide the compression stage with mechanical work produced during of relaxation.
- the invention uses centrifugal compression which makes it possible to reach significantly higher isothermal efficiencies (by example above 70% and typically close to 75-80%) despite relatively low compression ratios.
- the invention allows the active recovery of the expansion work, in particular of the cycle gas between 80K and 20K, which increases the efficiency of the installation.
- the compression of the cycle gas is entirely centrifugal and uses a cycle fluid mainly comprising helium or consisting of pure helium.
- a cycle fluid mainly comprising helium or consisting of pure helium.
- embodiments of the invention may include one or more of the following features:
- the invention also relates a process for producing hydrogen at cryogenic temperature, in particular liquefied hydrogen, using a device according to any one of the preceding characteristics or below, in which the pressure of the cycle gas at the inlet of the compression mechanism of the cycle gas is between two and forty bar abs and in particular between eight and thirty-five bar abs.
- the invention may also relate to any alternative device or method comprising any combination of the characteristics above or below within the scope of the claims.
- FIG. 1 represents a schematic and partial view illustrating a detail of the fourth possible embodiment of the invention illustrating an example of structure and possible operation of a motor-turbocompressor of the device.
- the device 1 for liquefying a fluid shown in is intended for the liquefaction of hydrogen but can be applied to other gases, in particular helium or any mixture.
- the device 1 comprises a circuit 3 of fluid to be cooled (typically hydrogen) having an upstream end intended to be connected to a source 2 of gaseous fluid and a downstream end 23 intended to be connected to a member 4 for collecting the fluid liquefied.
- the source 2 can typically comprise an electrolyser, a hydrogen distribution network, a methane reforming unit (SMR) or any other appropriate source(s).
- the device 1 comprises a set of heat exchangers 6, 7, 8, 9, 10, 11, 12, 13 arranged in series in heat exchange with the circuit 3 of the fluid to be cooled.
- the device 1 comprises at least a first cooling system 20 in heat exchange with at least a part of the set of heat exchangers 5, 6, 7, 8, 9, 10, 11, 12, 13.
- This first cooling system 20 is a refrigerator with a refrigeration cycle of a cycle gas mainly comprising helium.
- This refrigerator 20 comprising, arranged in series in a cycle circuit 14 (preferably closed in a loop): a mechanism 15 for compressing the cycle gas, at least one member 16, 5, 6, 8, 10, 12 for cooling the cycle gas, a cycle gas expansion mechanism 17 and at least one member 13, 12, 11, 10, 9, 8, 7, 6, 5 for heating the expanded cycle gas.
- the fluid to be liquefied is a fluid which is distinct from the cycle gas fluid (example helium and possibly other component(s)).
- these two circuits are therefore separate.
- the assembly of heat exchanger(s) which cools the hydrogen to be liquefied preferably comprises one or more countercurrent heat exchangers 5, 6, 8, 10, 12 arranged in series and in which two distinct portions of the cycle circuit 14 circulate simultaneously against the current (respectively for the cooling and the heating of distinct flows of the cycle gas).
- this plurality of counter-current heat exchangers forms both a member for cooling the cycle gas (after the compression and after the expansion stages for example) and a member for heating the cycle gas (after expansion and before returning to the compression mechanism).
- the compression mechanism comprises at least four compression stages composed of a set of centrifugal-type compressors arranged in series (and possibly in parallel).
- a compression stage 15 may be composed of a wheel of a motorized centrifugal compressor.
- the compression stages 15 (that is to say the compressor wheels) are mounted on shafts 19, 190 driven in rotation by a set of motor(s) 18 (at least one motor).
- all the compressors 15 are of the centrifugal type.
- the expansion mechanism for its part comprises at least three expansion stages formed by turbines 17 of the centripetal type arranged at least partly in series.
- the number of compression stages for example the number of compression wheels
- the number of expansion stages for example the number of expansion wheels
- all the turbines 17 are of the centripetal type and are mainly arranged in series.
- the at least one member 16, 5, 6, 8, 10, 12 for cooling the cycle gas is in particular configured to cool the cycle gas at the outlet of at least one of the turbines 17. say that, after expansion in a turbine 17, the cycle gas can be cooled by a value typically between 2K and 30K.
- At least one of the turbines 17 is coupled to the same shaft 19 as a compression stage 15 of a compressor so as to supply the compressor with the mechanical work produced during expansion.
- the device 1 can comprise one or more Moto-Turbo-Compressors on a part of the compressor station.
- a Moto-Turbo-Compressor is a set comprising an engine whose shaft directly drives a set of compression stage(s) (wheel(s)) and a set of expansion stage(s) (turbine(s) ). This enhances mechanical expansion work directly on one or more cycle gas compressors.
- the device 1 comprises more compression stages 15 than turbines 17, for example twice as many or approximately twice as many.
- Each turbine 17 can be coupled to the same shaft 19 as a single respective compressor wheel 15 driven by a respective motor 18.
- the other compressor wheel(s) 15 (stage(s)) not coupled to a turbine 17) can be mounted alone on rotary shafts 190 driven by respective separate motors 18 (Moto-compressor).
- the compression stages 15 coupled to a turbine 17 and the compressors not coupled to a turbine 17 can be alternated in series in the cycle circuit 14.
- the compression mechanism includes more than six compression stages in series.
- this is in no way limiting because it is possible to envisage, for example, a less efficient configuration with three compression stages in series which would make it possible to liquefy hydrogen.
- the minimum compression ratio (using centrifugal technology) to liquefy hydrogen should preferably be around 1.3 to 1.6.
- the device 1 could comprise eight compression stages 15 and four turbines 17. Any other distribution can be envisaged, for example sixteen compression stages 15 and eight turbines 17 or twelve stages compressor and six turbines or six compression stages and three turbines or four compressors and three turbines...
- Cooling may be provided downstream of all or part of the compression stages or downstream of all or part of the compressors 15 (for example via a heat exchanger 16 cooled by a heat transfer fluid or any other refrigerant). This cooling can be provided after each compression stage or, as illustrated, every two compression stages (or more) or only downstream of the compression station. Surprisingly, this distribution of the cooling not at the outlet of each of the compression stages 15 in series but every two (or three) compression stages 15 makes it possible to achieve cooling performance while limiting the costs of the device 1 .
- the at least one member for cooling the cycle gas preferably comprises a system 8, 10, 12 for cooling the cycle gas, such as a heat exchanger, arranged at the outlet of at least part of the 17 turbines in series.
- This intermediate inter-expansion cooling makes it possible to limit the value of the high pressure necessary to reach the coldest temperatures in the cycle gas.
- the device 1 preferably comprises a system for cooling the cycle gas, such as a heat exchanger, at the outlet of all the turbines 17 excluding the last turbine 17 in series according to the direction of circulation. cycle gas.
- this cooling system can be ensured by respective counter-current heat exchangers 8, 10, 12 mentioned above.
- This cooling after expansion allows a temperature staggering (i.e. reaching distinct temperatures lower and lower after each expansion stage) to extract cold from the fluid to be cooled.
- This staggering of temperatures is obtained by this arrangement and via a minimum compression ratio obtained to supply these various turbines 17.
- the arrangement of several centrifugal compression stages 15 in series upstream makes it possible to obtain this pressure differential allowing an adequate staging of the cooling downstream. Indeed, for the same pressure difference, the lower the temperature, the lower the enthalpy drop at constant entropy during expansion.
- the arrangement of the turbines 17 in series and the cooling 8, 10 at the outlet of the turbines has the effect of increasing the average mass flow rate of the turbines 17 compared to a conventionally known staging. The theoretical isentropic efficiency thus tends to increase and therefore makes it possible to achieve better turbine efficiencies 17.
- the 8, 10 cooling between expansion stages allows the cycle fluid to reach target liquefaction temperatures without requiring an even greater overall compression ratio.
- the expansions are preferably isentropic or quasi-isentropic. That is, the cycle fluid is cooled as it goes and the fluid liquefied.
- the minimum temperature is reached directly at the outlet of the last quasi-isentropic expansion stage (that is to say downstream of the last expansion turbine 17). It is therefore not necessary to provide an additional expansion valve of the Joule-Thomson type, for example, downstream.
- the cold and in particular a sub-cooling temperature of the hydrogen to be liquefied can be obtained exclusively with turbines 17 (working extraction).
- the majority or all of the turbines 17 are coupled with one or more compressors 15 respectively.
- the successive turbines 17 are preferably coupled respectively with compression stages 15 of compressors taken in the reverse order of their arrangement in series. That is to say that, for example, a turbine 17 is coupled with a compressor 15 located upstream of a compressor 15 coupled to the turbine 17 which precedes it.
- the order of association of the turbine 17 and coupled compressors is therefore preferably at least partially reversed between the turbines and the compressors (in the cycle circuit, a turbine further upstream is coupled with a compressor further downstream).
- the first turbine 17 (that is to say the first turbine 17 after the compression mechanism) can be coupled to the fifth compressor 15 in series (fifth compression stage) while the second turbine 17 can be coupled to the third compressor 15 in series (third compression stage), the third turbine 17 can be coupled to the first compressor 15 in series ( first compression stage).
- the other compressors 15 forming the other compression stages may not be coupled to a turbine (motor-compressor system and not motor-turbo-compressors).
- the most powerful turbine 17 can be coupled to the first compression stage (the first compression stage draws in the low pressure of the cycle). At this level of relative low pressure, the greater the compression ratio of the compressor 15, the less the impact of pressure drops at its level is felt (and so on with the other compressors 15).
- the turbines 17 could be coupled respectively to the compressors 15 of even order number (the first turbine with the sixth compressor, the second turbine with the fourth compressor, etc.) or with compressors directly in series (for example the first turbine 17 with the sixth compressor 15, the second turbine with the fifth compressor etc).
- the working pressures of the turbines 17 are set respectively on the working pressures of the compressors 15 to which they are coupled. That is, the pressure of the cycle gas entering the turbine 17 does not differ by more than 40% and preferably not more than 30 or 20% from the outlet pressure of the compressor 15 at which it is. coupled. This makes it possible to reduce the axial loads at the level of the output shafts 19 of the motors 18 concerned which directly couple the wheels of the compressors 15 and turbines 17.
- the at least one coupled turbine 17 and corresponding compression stage are structurally configured such that the cycle gas pressure exiting the turbine 17 differs by no more than 40% and preferably no more than 30%. % or not more than 20% of the cycle gas pressure at the inlet of the compression stage 15.
- the at least one turbine 17 and the corresponding coupled compression stage are preferably configured structurally also (or possibly alternatively) so that the pressure of the cycle gas which enters the turbine 17 does not differ by more than 40% and preferably not more than 30% or not more than 20% of the pressure of the cycle gas leaving the compression stage.
- This structural configuration of the turbine (for example turbine wheel) and compression stage (for example compression wheel) means that these two elements are dimensioned (shape and/or dimension of the wheel and/or of their volute and/or of their inlet distributor if applicable) to achieve respectively compressions and relaxations of the same absolute value or close as specified above. That is to say, by design, these two mated elements will be able to achieve these compression and expansion ratios (without using any other active or passive element in the cycle circuit), preferably whatever the flow conditions. cycle gas.
- the expansion rate at the terminals of the at least one turbine 17 coupled to a compression stage can be configured to achieve a pressure drop in the cycle gas of the value does not differ by more than 40% (or not more 20%) of the value of the pressure increase at the terminals of the compression stage 15 to which it is coupled.
- the compressor 15 is coupled to the turbine 17 and it works between 10 bar and 15 bar (compression of the flow initially at 10 bar at an outlet pressure of 15 bar), it is advantageous to have this flow expanded by the turbine 17 on pressures between 15 and 10 bar (inlet at 15bar and outlet at 10bar).
- the expansion mechanism may comprise at least two expansion stages in series composed of a set of turbines 17 of the centripetal type in series.
- At least two turbines 17 in series are coupled respectively with compression stages 15 taken in the reverse order of their arrangement in series. That is to say, at least one turbine 17 is coupled with a compression stage 15 located upstream of a compression stage 15 coupled to another turbine 17 which precedes it in the cycle circuit 14.
- the expansion rates chosen at the terminals of each turbine 17 are thus preferably imposed according to the compressor to which they are coupled (as explained above).
- the working pressures of the turbines 17 can be set to the working pressures of the compressors 15 "one by one". or "two by two" (i.e. the first turbine 17 works on the compression ratio of the 5th or 6th compressors 15; likewise the second turbine 17 works on the compression ratio of the 3rd or 4th compressors, etc. ...
- the first of these two compressors compresses for example the cycle gas at a first pressure PA while the second compresses this cycle gas then at a second pressure PB with PB > PA
- the turbine 17 which will be coupled to the first of these two compressors will preferentially expand the g cycle az from the second pressure PB to the first pressure PA. This can be obtained for example by adjusting the characteristics of this turbine 17 according to this constraint. For example, there is adjustment of the section of the distributor calibrating the flow arriving at the turbine 17, which has an effect on the pressure drop occurring in the distributor part and the impeller part of the turbine.
- the mechanical coupling or couplings of the turbines 17 and compressor wheels 15 to the same shaft 19 is (are) configured to preferably ensure an identical speed of rotation of the turbine 17 and the coupled compressor wheels 15 . This makes it possible to obtain a direct and effective valuation of the work of relaxation in the device. If necessary, the speeds of rotation of all the wheels of compressors and turbines can be equal to one and the same determined value.
- a control member can optionally be provided for all or part of the compression stages.
- a variable frequency drive (VFD”) can be provided for each motor 18 driving at least one compression stage. This makes it possible to independently adjust the speeds of several or each compression stage and therefore the rebound without using a complex gear system or motorization and specific control means linked to variable blades upstream of one or more stages. compression.
- This speed control device can be provided for all the compressors or for each compression stage.
- the device 1 does not include a flow valve or valve for reducing the pressure in the circuit (pressure drop) between the compression stages, between the expansion stages or downstream of the cycle expansion.
- a flow valve or valve for reducing the pressure in the circuit (pressure drop) between the compression stages, between the expansion stages or downstream of the cycle expansion can be provided in the cycle circuit 14 .
- the operating point of the turbines 17 can be adjusted solely by the dimensional characteristics of the turbine 17 (no throttling valve at the turbine inlet for example).
- This increases the reliability of the device (no potential problem of failure of control valves on the process, because they are absent).
- This also allows the elimination of costly ancillary circuits (safety valves, etc.) and simplifies manufacturing (reduction in the number of lines to be insulated, etc.).
- a helium-based cycle gas makes it possible to reach temperatures with a view to sub-cooling the liquefied hydrogen without the risk of a sub-atmospheric zone in the process (which would be dangerous if fluid cycle was hydrogen) and without risk of freezing the cold source (the maximum liquefaction temperature of helium is equal to 5.17K).
- the sub-cooling effect of liquefied hydrogen has a very significant advantage on the transport chain of the hydrogen molecule and then potentially among users (typically liquid stations) thanks to the reduction of vaporization gases ("Boil-off" ) during trips.
- the low pressure portion of cycle circuit 14 can be operated at relatively high pressure. This makes it possible to reduce the volume flows in the heat exchangers 6, 7, 8, 9, 10, 11, 12, 13.
- the working pressure of the cycle gas can thus be decorrelated from the target pressure or temperature fluid to be cooled. This pressure of the cycle gas can thus be increased to adapt to the constraints of the turbomachine but also to reduce the volume flow at low pressure which is, as a general rule, one of the major parameters sizing the heat exchangers.
- This low pressure level in the cycle circuit 14 is for example greater than or equal to 10 bar and can typically be between 10 and 40 bar. This decreases the volume flow in the heat exchangers which counteracts the low compression ratio per compression stage.
- the device 1 may comprise a second cooling system in heat exchange with at least part of the set of heat exchanger(s) 5 in exchange with the cycle gas for example.
- This second cooling system 21 comprises for example a heat transfer fluid circuit 25 such as liquid nitrogen or a mixture of refrigerants which cools the cycle gas and/or the hydrogen to be liquefied through the first or first heat exchangers. counter-current heat, and can also make it possible to combat losses due to the difference at the hot end caused by the circulation in a closed loop of the heat transfer fluid(s), as illustrated in the via at least one pre-cooling exchanger 5.
- a heat transfer fluid circuit 25 such as liquid nitrogen or a mixture of refrigerants which cools the cycle gas and/or the hydrogen to be liquefied through the first or first heat exchangers. counter-current heat, and can also make it possible to combat losses due to the difference at the hot end caused by the circulation in a closed loop of the heat transfer fluid(s), as illustrated in the via at least one pre-cooling exchanger 5.
- This second cooling system 21 makes it possible, for example, to pre-cool the fluid to be liquefied and/or the working gas at the outlet of the compression mechanism.
- This coolant which circulates in the heat transfer fluid circuit 25 (for example in a loop) is for example supplied by a unit 27 for the production and/or storage 28 of this coolant. If necessary, the fluid circuit 3 to be cooled passes through this unit 27 for upstream pre-cooling.
- the device 1 it is possible for the device 1 to have other additional cooling system(s).
- a third cooling circuit supplied by a cooling unit for example providing a cold source at a temperature typically between 5° C. and -60° C.
- a third cooling circuit supplied by a cooling unit for example providing a cold source at a temperature typically between 5° C. and -60° C.
- a fourth cooling system could also be provided to further supply cold to device 1 and increase the liquefaction power of device 1 if necessary.
- the embodiment of the differs from the previous one only in that the cycle circuit 14 comprises a return line 22 having a first end connected to the outlet of one of the turbines 17 (other than the last one downstream) and a second end connected to the inlet one of the compressors 15 other than the first compressor 15 (upstream).
- This return line 22 makes it possible to return part of the flow of cycle gas to the compression mechanism at an intermediate pressure level between the low pressure at the inlet of the compression mechanism and the high pressure at the outlet of the compression mechanism.
- the return pipe 22 can be in heat exchange with at least some of the counter-current heat exchangers.
- Several return lines to the intermediate pressure compressor station can advantageously be installed depending on the expected level of optimization of the process.
- the sampling points (at the level of the turbines considered) and injection points (at the level of the compression stages considered) can be located at different pressure levels.
- the embodiment of the differs from the previous one only in that the cycle circuit 14 further comprises a partial bypass pipe 24 having a first end connected upstream of a turbine 17 (for example the first turbine 17 upstream) and a second end connected to the entry of another turbine 17 located downstream (for example the third turbine).
- the diversion pipe 24 allows the diversion of part of the cycle gas flow exiting at high pressure from the compression mechanism towards the coldest turbines further downstream. The rest of the flow passes through this first turbine 17 upstream which is hotter.
- the compressors located at higher pressure suck in a lower volume flow than the first compression stages (located close to the low pressure of the process).
- a way to increase this volume flow and thus potentially increase their isentropic efficiency is to integrate an intermediate pressure return from the expansion stages as shown in the .
- the device 1 shown in illustrates yet another non-limiting embodiment. Elements identical to those described above are designated by the same reference numerals and are not described in detail again.
- the cycle circuit 14 of the device of the includes three compressors (driven by three motors 18 respectively). As illustrated, each compressor may have four stages of compression (i.e., four compression wheels in series). These compressor wheels 15 can be mounted by direct coupling to one end of a shaft 19 of the motor 18 concerned. In this example, the device therefore has twelve stages of centrifugal compression in series. As shown, cooling 26 of the cycle gas can be provided for every two compression stages.
- the device 1 has in this example five expansion stages in series (six centripetal turbine wheels, two of which are arranged in parallel), for example one or two expansion stages per compressor.
- all the turbines 17 can be coupled to a compressor shaft 19 (for example two turbines 17 are mounted at the other end of the shaft 19 of each motor 18 to provide mechanical work to the compressor wheels 15 also mounted on this tree 19).
- the turbines 17 could be on the same side of the shaft 19 as the wheels 15 of compression.
- the first four expansion stages are formed by four turbines 17 in series.
- the fifth expansion stage is for example formed of two turbines 17 arranged respectively in two parallel branches of the circuit 14 of the cycle.
- the device 1 shown in differs from that of the in that it comprises cycle gas return lines 122, 123, 124 transferring part of the cycle gas leaving the turbines 17 at intermediate pressure levels (medium pressure) within the compression mechanism.
- a line 124 connects the output of the first turbine to the output of the eighth compression stage.
- a line 123 connects the outlet of the second turbine to the outlet of the sixth compression stage.
- a line 122 connects the outlet of the third turbine 17 to the outlet of the fourth compression stage.
- the device could comprise only one or only two of these medium-pressure return lines.
- other return lines could be considered.
- the ends of these lines could be changed (outlet from other turbine(s) and outlet(s) from other compression stages).
- the device 1 shown in illustrates a detail of the device 1 illustrating a non-limiting example of structure and possible operation of a motor-turbocompressor arrangement.
- One end of shaft 19 of motor 18 drives four compressor wheels (four compression stages 15).
- the other end of shaft 19 is directly coupled to two expansion stages (two turbines 17).
- any other appropriate type of arrangement of the compression stages 15 and expansion stage 17 can be considered (idem for the number of engines).
- the last two expansion stages can be installed in parallel and not in series. This allows for a greater enthalpy drop at the terminals of these turbines. This would be achieved at the expense of efficiency (because two turbines would share 100% of the flow and the available pressure difference would be almost doubled). Despite this potential drop in efficiency for these last two expansion stages, achieving a greater enthalpy drop could make it possible to stage the expansion more effectively.
- the same cold enthalpy differential induces a lower temperature variation at the terminals of a turbine than for a hotter turbine. This improves the efficiency of the refrigeration and liquefaction process.
- the efficiency of the device makes it possible to liquefy hydrogen with good energy efficiency.
- the temperature differential caused by the turbine 17 can be a function of the temperature of the cycle gas upstream of the turbine 17.
- a buffer tank (not shown) and a set of valve(s) can be provided, preferably at the low pressure level, in order to limit the maximum gas filling pressure of the cooling circuit.
- the minimum compression rate is between 1.3 and 1.6 at the terminals of the compressor station.
- the cycle gas can be composed of 100% or 99% helium and supplemented with hydrogen for example.
- the cycle circuit may comprise at the inlet of at least one of the turbines 17 an inlet guide device ("IGV” or “Inlet Guide Vane”) configured to adjust the flow rate of fluid at a determined operating point.
- IGV inlet guide device
- compressor wheels 15 and/or turbines 17 is not limited to the previous examples.
- the number and the arrangement of the compressors 15 can be modified.
- the compression mechanism could be composed of only three compressors, each compressor could be provided with several stages of compression for example three stages of compression i.e. three compressor wheels (with or without inter-stage cooling ).
- two compression stages 15 could be arranged in parallel and in series with other compression stages (for example three in series).
- the two compression stages in parallel can be placed upstream of the others and thus provide downstream a relatively high flow rate at low pressure using machines which may all be identical.
- turbines 17 can be placed in parallel in the circuit 14 of the cycle.
- all the turbines could be coupled to one or more compressor wheels (for example one or more turbines 17 coupled to the same shaft 19 as one or more compression stages).
- the circuit 3 of the fluid to be cooled can comprise one or more catalysis devices (pot(s) 280) apart from exchangers or section(s) 29 of exchanger(s)) for example for the conversion of hydrogen (ortho to para).
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Abstract
Description
- le mécanisme de compression comprend uniquement des compresseurs de type centrifuge,
- le au moins un organe de refroidissement du gaz de cycle comprend un ensemble d’échangeur(s) de chaleur disposé(s) à la sortie d’au moins une partie des turbines,
- le dispositif comprend un système de refroidissement du gaz de cycle, tel qu’un échangeur de chaleur, disposé à la sortie d’au moins une partie des turbines à l’exclusion de la dernière turbine en série selon le sens de circulation du gaz de cycle,
- selon le sens de circulation du gaz de cycle, au moins deux turbines en série sont accouplées respectivement avec des étages de compression pris dans l’ordre inverse de leur disposition en série, c’est-à-dire que, par exemple, au moins une turbine est accouplée avec un étage de compression située en amont d’un étage de compression accouplé à une autre turbine qui la précède dans le circuit de cycle,
- la pression de travail d’au moins une turbine accouplée à un étage de compression est réglée sur la pression de travail du compresseur comprenant l’étage de compression auquel elle est accouplée, c’est-à-dire que la pression du gaz de cycle qui entre dans la turbine ne diffère pas plus de 40% et de préférence de pas plus de 30% ou de 20% de la pression d’entrée du compresseur auquel elle est accouplée,
- l’accouplement mécanique des turbines et des étages de compression à un même arbre est configuré pour assurer une vitesse de rotation identique de la turbine et des étages de compression accouplés,
- le dispositif comprend plus d’étages de compression que de turbines, chaque turbine étant accouplée au même arbre qu’un unique étage de compression respectif entraîné par un moteur respectif, les autres étages de compression non accouplés à une turbine étant montés seuls sur des arbres rotatifs entraînés par des moteurs respectifs distincts,
- les étages de compression accouplés à une turbine et les étages de compression non accouplés à une turbine sont alternés en série dans le circuit de cycle,
- le dispositif comprend seize étages de compression et huit turbines ou douze étages de compression et six turbines ou huit étages de compression et quatre turbines ou six étages de compression et trois turbines ou quatre étages de compression et trois turbines,
- le circuit de cycle comprend une conduite de renvoi ayant une première extrémité reliée à la sortie d’une des turbines et une seconde extrémité reliée à l’entrée d’un des étages de compression autre que le premier étage de compression, pour renvoyer une partie du flux de gaz de cycle dans le mécanisme de compression à un niveau de pression intermédiaire entre la pression basse en entrée du mécanisme de compression et la pression plus haute en sortie du mécanisme de compression,
- la conduite de renvoi est en échange thermique avec le au moins un organe de refroidissement du gaz de cycle et/ou l’organe de réchauffage du gaz de cycle détendu,
- le circuit de cycle comprend une conduite de dérivation partielle du flux de gaz de cycle ayant une première extrémité reliée en amont d’une turbine et une seconde extrémité reliée à l’entrée d’une autre turbine située en aval, ladite conduite de dérivation étant configurée pour transférer une partie du flux de gaz de cycle directement à l’entrée de la turbine aval plus froide,
- l’ensemble d’échangeur(s) de chaleur comprend une pluralité d’échangeurs de chaleur disposés en série et dans lesquels deux portions distinctes du circuit de cycle circulent simultanément à contre-courant pour respectivement le refroidissement et pour le réchauffage du gaz de cycle, ladite pluralité d’échangeurs de chaleur formant un organe de refroidissement du gaz de cycle et un organe de réchauffage du gaz de cycle,
- le dispositif comprend un second système de refroidissement en échange thermique avec au moins une partie de l’ensemble d’échangeur(s) de chaleur, ledit second système de refroidissement comprenant un circuit de fluide caloporteur tel que de l’azote liquide ou un mélange de réfrigérants,
- le gaz de cycle est constitué d’hélium ou un mélange comprenant au moins 50% d’hélium,
- le circuit de cycle comprend à l’entrée d’au moins une des turbines un dispositif de guide d’entrée (« IGV » ou « Inlet Guide Vane ») configuré pour régler le débit de fluide à un point de fonctionnement déterminé,
- les pressions de travail des turbines sont calées respectivement sur les pressions de travail des compresseurs auxquelles elles sont accouplées, de sorte que la pression du gaz de cycle qui entre dans la turbine ne diffère pas plus de 30% et de préférence de pas plus de 20% de la pression de sortie de deux compresseurs en série auquel(s) elle est accouplée
Claims (16)
- Dispositif de liquéfaction d’un fluide tel que l’hydrogène et/ou l’hélium comprenant un circuit (3) de fluide à refroidir ayant une extrémité amont destinée à être reliée à une source (2) de fluide gazeux et une extrémité aval (23) destinée à être reliée à un organe (4) de collecte du fluide liquéfié, le dispositif (1) comprenant un ensemble d’échangeur(s) (6, 7, 8, 9, 10, 11, 12, 13) de chaleur en échange thermique avec le circuit (3) de fluide à refroidir, le dispositif (1) comprenant au moins un premier système (20) de refroidissement en échange thermique avec au moins une partie de l’ensemble d’échangeur(s) (6, 7, 8, 9, 10, 11, 12, 13) de chaleur, le premier système (20) de refroidissement étant un réfrigérateur à cycle de réfrigération d’un gaz de cycle comprenant majoritairement de l’hélium, ledit le réfrigérateur (20) comprenant, disposés en série dans un circuit (14) de cycle : un mécanisme (15) de compression du gaz de cycle, au moins un organe (16, 5, 6, 8, 10, 12) de refroidissement du gaz de cycle, un mécanisme (17) de détente du gaz de cycle et au moins un organe (13, 12, 11, 10, 9, 8, 7, 6, 5) de réchauffage du gaz de cycle détendu, dans lequel le mécanisme de compression comprend au moins quatre étages de compression (15) en série composés d’un ensemble de compresseur(s) (15) de type centrifuge, les étages de compressions (15) étant monté sur des arbres (19, 190) entraînés en rotation par un ensemble de moteur(s) (18), le mécanisme de détente comprenant au moins trois étages de détente en série composés d’un ensemble de turbines (17) de type centripète, le au moins un organe (16, 5, 6, 8, 10, 12) de refroidissement du gaz de cycle étant configuré pour refroidir le gaz de cycle à la sortie de l’une au moins des turbines (17) et dans lequel au moins une des turbines (17) est accouplée au même arbre (19) qu’au moins un étage de compression (15) de façon à fournir à l’étage de compression (15) du travail mécanique produit lors de la détente.
- Dispositif selon la revendication 1, caractérisé en ce que le mécanisme de compression comprend uniquement des compresseurs (15) de type centrifuge.
- Dispositif selon la revendication 1 ou 2, caractérisé en ce que le au moins un organe de refroidissement du gaz de cycle comprend un ensemble d’échangeur(s) de chaleur (8, 10, 12) disposé(s) à la sortie d’au moins une partie des turbines (17).
- Dispositif selon l’une quelconque des revendications 1 à 3, caractérisé en ce qu’il comprend un système (8, 10, 12) de refroidissement du gaz de cycle, tel qu’un échangeur de chaleur, disposé à la sortie d’au moins une partie des turbines (17) à l’exclusion de la dernière turbine (17) en série selon le sens de circulation du gaz de cycle.
- Dispositif selon l’une quelconque des revendications 1 à 4, caractérisé en ce que, selon le sens de circulation du gaz de cycle, au moins deux turbines (17) en série sont accouplées respectivement avec des étages de compression (15) pris dans l’ordre inverse de leur disposition en série, c’est-à-dire que, par exemple, au moins une turbine (17) est accouplée avec un étage de compression (15) située en amont d’un étage de compression (15) accouplé à une autre turbine (17) qui la précède dans le circuit (14) de cycle.
- Dispositif selon l’une quelconque des revendications 1 à 5, caractérisé en ce que la pression de travail d’au moins une turbine (17) accouplée à un étage de compression (15) est réglée sur la pression de travail du compresseur (15) comprenant l’étage de compression auquel elle est accouplée, c’est-à-dire que la pression du gaz de cycle qui entre dans la turbine (17) ne diffère pas plus de 40% et de préférence de pas plus de 30% ou de 20% de la pression d’entrée du compresseur (15) auquel elle est accouplée.
- Dispositif selon l’une quelconque des revendications 1 à 6, caractérisé en ce que l’accouplement mécanique des turbines (17) et des étages de compression (15) à un même arbre (19) est configuré pour assurer une vitesse de rotation identique de la turbine (17) et des étages de compression (15) accouplés.
- Dispositif selon l’une quelconque des revendications 1 à 7, caractérisé en ce qu’il comprend plus d’étages de compression (15) que de turbines (17), chaque turbine (17) étant accouplée au même arbre (19) qu’un unique étage de compression (15) respectif entraîné par un moteur (18) respectif, les autres étages de compression (15) non accouplés à une turbine (17) étant montés seuls sur des arbres (190) rotatifs entraînés par des moteurs (18) respectifs distincts.
- Dispositif selon la revendication 8, caractérisé en ce que les étages de compression (15) accouplés à une turbine (17) et les étages de compression non accouplés à une turbine (17) sont alternés en série dans le circuit de cycle.
- Dispositif selon l’une quelconque des revendications 1 à 9, caractérisé en ce qu’il comprend seize étages de compression (15) et huit turbines (17) ou douze étages de compression (15) et six turbines (17) ou huit étages de compression (15) et quatre turbines (17) ou six étages de compression (15) et trois turbines (17) ou quatre étages de compression (15) et trois turbines (17).
- Dispositif selon l’une quelconque des revendications 1 à 10, caractérisé en ce que le circuit (14) de cycle comprend une conduite (22) de renvoi ayant une première extrémité reliée à la sortie d’une des turbines (17) et une seconde extrémité reliée à l’entrée d’un des étages de compression (15) autre que le premier étage de compression (15), pour renvoyer une partie du flux de gaz de cycle dans le mécanisme de compression à un niveau de pression intermédiaire entre la pression basse en entrée du mécanisme de compression et la pression plus haute en sortie du mécanisme de compression.
- Dispositif selon la revendication 11, caractérisé en ce que la conduite (22) de renvoi est en échange thermique avec le au moins un organe (5, 6, 8, 10, 12) de refroidissement du gaz de cycle et/ou l’organe (13, 12, 11, 10, 9, 8, 7, 6, 5) de réchauffage du gaz de cycle détendu.
- Dispositif selon l’une quelconque des revendications 1 à 12, caractérisé en ce que le circuit (14) de cycle comprend une conduite (24) de dérivation partielle du flux de gaz de cycle ayant une première extrémité reliée en amont d’une turbine (17) et une seconde extrémité reliée à l’entrée d’une autre turbine (17) située en aval, ladite conduite (24) de dérivation étant configurée pour transférer une partie du flux de gaz de cycle directement à l’entrée de la turbine aval plus froide.
- Dispositif selon l’une quelconque des revendications 1 à 13, caractérisé en ce que l’ensemble d’échangeur(s) de chaleur comprend une pluralité d’échangeurs de chaleur (5, 6, 7, 8, 9, 10, 11, 12, 13) disposés en série et dans lesquels deux portions distinctes du circuit (14) de cycle circulent simultanément à contre-courant pour respectivement le refroidissement et pour le réchauffage du gaz de cycle, ladite pluralité d’échangeurs de chaleur formant un organe de refroidissement du gaz de cycle et un organe (16, 5, 6, 8, 10, 12) de réchauffage du gaz de cycle.
- Dispositif selon l’une quelconque des revendications 1 à 14, caractérisé en ce qu’il comprend un second système de refroidissement en échange thermique avec au moins une partie de l’ensemble d’échangeur(s) (5, 6, 7, 8, 9, 10, 11, 12, 13) de chaleur, ledit second système (21) de refroidissement comprenant un circuit (25) de fluide caloporteur tel que de l’azote liquide ou un mélange de réfrigérants.
- Procédé de production d’hydrogène à température cryogénique, notamment d’hydrogène liquéfié, utilisant un dispositif (1) selon l’une quelconque des revendications précédentes, dans lequel la pression du gaz de cycle à l’entrée du mécanisme (15) de compression du gaz de cycle est compris entre deux et quarante bar abs et notamment comprise entre à huit et trente-cinq bar abs.
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KR1020237030204A KR20230144565A (ko) | 2021-02-10 | 2022-01-18 | 수소 및/또는 헬륨과 같은 유체를 액화하기 위한 장치 및 방법 |
JP2023541739A JP2024508598A (ja) | 2021-02-10 | 2022-01-18 | 水素及び/又はヘリウムなどの流体を液化するためのデバイス及び方法 |
CN202280009325.9A CN116745569A (zh) | 2021-02-10 | 2022-01-18 | 用于液化诸如氢气和/或氦气的流体的装置和方法 |
EP22700817.4A EP4291837A1 (fr) | 2021-02-10 | 2022-01-18 | Dispositif et procédé de liquéfaction d'un fluide tel que l'hydrogène et/ou de l'hélium |
US18/276,799 US20240125547A1 (en) | 2021-02-10 | 2022-01-18 | Device and method for liquefying a fluid such as hydrogen and/or helium |
CA3205740A CA3205740A1 (fr) | 2021-02-10 | 2022-01-18 | Dispositif et procede de liquefaction d'un fluide tel que l'hydrogene et/ou de l'helium |
AU2022219411A AU2022219411A1 (en) | 2021-02-10 | 2022-01-18 | Device and method for liquefying a fluid such as hydrogen and/or helium |
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FR2101243A FR3119667B1 (fr) | 2021-02-10 | 2021-02-10 | Dispositif et procédé de liquéfaction d’un fluide tel que l’hydrogène et/ou de l’hélium |
FRFR2101243 | 2021-02-10 |
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PCT/EP2022/050973 WO2022171390A1 (fr) | 2021-02-10 | 2022-01-18 | Dispositif et procédé de liquéfaction d'un fluide tel que l'hydrogène et/ou de l'hélium |
PCT/EP2022/050974 WO2022171391A1 (fr) | 2021-02-10 | 2022-01-18 | Dispositif et procédé de liquéfaction d'un fluide tel que l'hydrogène et/ou de l'hélium |
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FR3098574B1 (fr) * | 2019-07-10 | 2021-06-25 | Air Liquide | Dispositif de réfrigération et/ou de liquéfaction |
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2022
- 2022-01-18 US US18/276,853 patent/US20240151464A1/en active Pending
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- 2022-01-18 EP EP22700819.0A patent/EP4291839A1/fr active Pending
- 2022-01-18 CN CN202280010493.XA patent/CN116783439A/zh active Pending
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- 2022-01-18 KR KR1020237030204A patent/KR20230144565A/ko unknown
- 2022-01-18 KR KR1020237030206A patent/KR20230144567A/ko unknown
- 2022-01-18 EP EP22700818.2A patent/EP4291838A1/fr active Pending
- 2022-01-18 JP JP2023543080A patent/JP2024505822A/ja active Pending
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- 2022-01-18 CA CA3205740A patent/CA3205740A1/fr active Pending
- 2022-01-18 EP EP22700817.4A patent/EP4291837A1/fr active Pending
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WO2022171392A1 (fr) | 2022-08-18 |
FR3119667B1 (fr) | 2023-03-24 |
EP4291839A1 (fr) | 2023-12-20 |
KR20230144568A (ko) | 2023-10-16 |
AU2022219166A1 (en) | 2023-09-21 |
CN116745569A (zh) | 2023-09-12 |
JP2024505822A (ja) | 2024-02-08 |
KR20230144565A (ko) | 2023-10-16 |
US20240125547A1 (en) | 2024-04-18 |
EP4291837A1 (fr) | 2023-12-20 |
US20240142170A1 (en) | 2024-05-02 |
KR20230144567A (ko) | 2023-10-16 |
AU2022220636A1 (en) | 2023-07-27 |
AU2022219411A1 (en) | 2023-09-07 |
CA3205741A1 (fr) | 2022-08-18 |
JP2024508598A (ja) | 2024-02-28 |
CN116783439A (zh) | 2023-09-19 |
CA3205738A1 (fr) | 2022-08-18 |
EP4291838A1 (fr) | 2023-12-20 |
WO2022171391A1 (fr) | 2022-08-18 |
CN116761973A (zh) | 2023-09-15 |
FR3119667A1 (fr) | 2022-08-12 |
US20240151464A1 (en) | 2024-05-09 |
JP2024505815A (ja) | 2024-02-08 |
CA3205740A1 (fr) | 2022-08-18 |
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