CN1683844A - Multi-pressure-level mixed working medium cryogenic throttling refrigeration system - Google Patents
Multi-pressure-level mixed working medium cryogenic throttling refrigeration system Download PDFInfo
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- CN1683844A CN1683844A CN 200410031158 CN200410031158A CN1683844A CN 1683844 A CN1683844 A CN 1683844A CN 200410031158 CN200410031158 CN 200410031158 CN 200410031158 A CN200410031158 A CN 200410031158A CN 1683844 A CN1683844 A CN 1683844A
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Classifications
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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
- F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
- F25J1/02—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
- F25J1/0211—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
- F25J1/0212—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 single flow MCR cycle
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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
- F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
- F25J1/0002—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the fluid to be liquefied
- F25J1/0022—Hydrocarbons, e.g. natural gas
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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
- F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
- F25J1/003—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
- F25J1/0047—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
- 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
- F25J1/0055—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 originating from an incorporated cascade
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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
- F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
- F25J1/006—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the refrigerant fluid used
- F25J1/0097—Others, e.g. F-, Cl-, HF-, HClF-, HCl-hydrocarbons etc. or mixtures thereof
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Chemical Kinetics & Catalysis (AREA)
- General Chemical & Material Sciences (AREA)
- Oil, Petroleum & Natural Gas (AREA)
- Separation By Low-Temperature Treatments (AREA)
Abstract
A multi-pressure-level mixed working medium cryogenic throttling refrigeration system comprises a multi-stage compressor unit MCPU, a regenerative precooling unit MRU and an evaporator unit EVU. The connection mode is as follows: a high-pressure outlet CPHO of the multi-stage compressor unit MCPU is connected with a high-pressure inlet MPHI of the regenerative pre-cooling unit MRU, and a low-pressure inlet CPLI of the multi-stage compressor unit MCPU is connected with a low-pressure outlet MPLO of the regenerative pre-cooling unit MRU; and a high-pressure outlet MPHO of the regenerative pre-cooling unit MRU is connected with an inlet EVI of the evaporator unit EVU, and an outlet EVO of the evaporator unit EVU is connected with a low-pressure inlet MPLI of the regenerative pre-cooling unit MRU. By adopting the high-efficiency multi-element mixed working medium, the refrigeration system reduces the irreversible loss in the compression and heat return processes from the thermodynamic property and reduces the loss in the actual flowing and heat exchange processes, thereby having high thermodynamic efficiency and being particularly suitable for the fields of large and medium low-temperature refrigeration and gas liquefaction.
Description
Technical field
The present invention relates to low-temperature refrigeration technology and gas liquefaction field, particularly a kind of multiple pressure grade mixed working medium cryogenic throttling refrigeration.
Background technology
Take the Cryogenic mixed-refrigerants j-t refrigerator of backheat measure to be widely used in the energy, chemical industry and cryogenic engineering field, be used for realizing the aspects such as liquefaction of device cooling and industrial gasses, wherein the application in the liquefied natural gas field is one of most important embodiment of mixed work medium for throttling Refrigeration Technique. The employing of multicomponent mixture working medium makes the refrigeration machine design and running have the more selection free degree. Therefore, for difference cooling object and application requirements, various cooling flow system occurred, only just had with the liquefied natural gas field to be no less than tens of kinds of Process flows and to occur. The appearance of these refrigeration systems is based on and raises the efficiency, reduces cost and reduces the different requirements such as system complexity and propose. And above-mentioned requirements also is the promotion power that new cooling flow constantly occurs.
Cast aside the details in all mixed work medium for throttling cooling flows, the common trait of existing mixed working substance copious cooling throttle cooling flow is exactly: utilize compressor that multicomponent mixture work medium is compressed to a pressure level, through cooler the heat of compression is taken away; The high pressure mixing working medium that returns to environment temperature enters the dividing wall type heat exchanger low pressure mixed working fluid cooling of being backflowed, then enter throttle expansion valve and realize throttling refrigeration, mixed working fluid self pressure decreased to one low-pressure stage, enter evaporimeter and provide cold for the object that is cooled, then enter heat exchanger cooling high pressure incoming flow mixed working fluid; Self temperature is recovered near room temperature, enters compressor, finishes a kind of refrigeration cycle. Above-mentioned circulation continuous carries out just can providing continuously cold at design temperature. From thermodynamics, mixed working fluid has experienced respectively 4 stages at said process: compression stage (comprising the condensation exothermic process), in the backheat stage, throttling expansion stage and cold provide the stage. For the different application requirement, each stage may overlap, for example in the gas liquefaction stage, cold provides not only the evaporimeter in minimum temperature, but be combined with each other with the backheat stage, the low-temp low-pressure working medium of namely backflowing provides cold for incoming flow high-pressure working medium and cooled object (such as natural gas) simultaneously. Therefore, prior art is that the one-level compression namely exists high pressure (generally in 1.8～2.5MPa scope) and two pressure stages of low pressure (generally in 0.1～0.7MPa scope) substantially.
Described heat recovery process is actual to be circularly cooling working medium mesolow fluid cooling high-pressure fluid, high-pressure working medium temperature before throttling is reduced, thereby reduce the process of restriction loss, in this process, low pressure working fluid is passed to high-pressure working medium with cold, and self temperature is recovered near environment temperature. Theoretical according to low temperature thermodynamic, heat recovery process efficient be the key factor that affects the refrigeration system overall efficiency. For refrigeration working medium of the same race, in gas phase zone, because the impact of pressure comparison heat, the specific heat of high-pressure fluid is greater than the specific heat of low-pressure fluid, be that the heat equivalent of high-pressure working medium under the same traffic is always greater than the heat equivalent of low-pressure fluid, therefore high and low pressure both sides heat equivalent always can not finely be mated in the Recuperative heat exchanger, this has just caused in the Recuperative heat exchanger on the cold and hot two fluid streams thermodynamics intrinsics heat exchange not mate, cause the backheat loss, this has not been the problem that can solve by the measure of thermal conduction study augmentation of heat transfer. At two-phase section, latent heat of phase change has very big contribution (zeotrope) to equivalent specific heat, and the latent heat of phase change higher pressure working medium of identical working medium low-pressure fluid is large, therefore at two-phase section the low-pressure fluid heat equivalent is increased. Therefore. Solve the interior unmatched way of heat equivalent of Recuperative heat exchanger and have such two kinds: the first is by adjusting the mixture constituent element, the transition temperature area that changes the high-low pressure both sides is regulated both sides fluid specific heat, make interior two side liquids of Recuperative heat exchanger be in two-phase section as far as possible, this need to increase higher boiling constituent element matched proportion density (such as patent application: 03121422, publication number: CN1462861A, public luxuriant fine jade etc., 2003); The secondth, adopt the measure that is separated, reduce the high-pressure side fluid flow, the phase that will be in the high-pressure fluid of two-phase section separates, gas phase enters Recuperative heat exchanger and further cools off, liquid phase is directly throttling expansion then, realizes that refrigeration effect enters low-pressure side cooling gas-phase working medium (as: Missimer, D.J., US patent 3698202,1972). Above-mentioned two measures are specific heat and flows of regulating respectively in two parameters of heat equivalent. The critical components such as compressor that corresponding separately system adopts, above-mentioned two kinds of methods all can have the higher thermal mechanical efficiency, especially the first measure through optimal design.
But for the cryogenic refrigeration warm area,, increase the higher boiling constituent element and might cause occurring higher boiling constituent element and lubricating oil frozen plug restricting element to 120K such as 80K, especially limitting (80K) near low temperature. In addition, adopt single-stage compressor to realize cryogenic refrigeration, for improving compressor operating efficient, reduce pressure ratio, improve low pressure, often need in mixed working fluid, add more lower boiling constituent element such as neon and helium, and helium is negative (temperature raises after being throttling) in this warm area throttle effect, the neon throttle effect is very little, more seriously at above-mentioned warm area, no matter these two kinds of gases of neon helium are to be non-condensable gas at high pressure or at the low pressure runner, the heat exchange property of this refrigeration system inside that deteriorates significantly. Another aspect, single-stage compressor generally be applied in middle-size and small-size refrigeration system, and in big-and-middle-sized refrigerating plant, compound compressor is adopted in especially natural gas liquid chemical industry more because pressure ratio and power are all restricted.
In addition, for realizing 210～230K refrigeration, often adopt two stages of compression two-stage throttling refrigeration circulation (Li Songshou etc. in general cold field, Refrigeration Principle ﹠ Equipment, Shanghai science tech publishing house, 1988, pp.57-59), main purpose is to solve the excessive problem of compressor pressure ratio when realizing low temperature. Also there be in addition twice circulating with choke (Chen Guobang etc. to occur in the deep cooling field, China Machine Press, 1994, pp.328-329), adopt pure working medium, mainly reduce the front temperature of afterbody throttling, but pressure is through a throttling before the afterbody throttling, pressure reduction reduces before and after making throttling, can reduce the isothermal throttle effect of specific discharge.
Summary of the invention
The object of the invention is to overcome many problems that prior art exists in realizing cryogenic refrigeration, better realize heat equivalent coupling in the Recuperative heat exchanger and a plurality of pressure stages of providing of good utilisation compound compressor more, and a kind of multiple pressure grade mixed working medium cryogenic throttling refrigeration is provided; Can be widely used in and satisfy various deep cooling demand occasions, such as gas liquefaction, particularly natural gas liquefaction, air separation, chemical industry tail gas liquefaction recovery, associated gas, coal gas gasification etc.; Also can be applied to cooling high-temperature superconducting device, the cooling of cold neutron source methane moderator, ultrahigh vacuum steam cold-trap etc., have extensive and important meaning.
Implementer's case of the present invention is as follows:
Multiple pressure grade mixed working medium cryogenic throttling refrigeration provided by the invention is comprised of multi-stage compression unit unit MCPU, backheat precooling unit MRU and evaporator unit EVU; Its connected mode is: the high-pressure outlet CPHO of multi-stage compression unit unit MCPU connects the high pressure entry MPHI of backheat precooling unit MRU, and the low-pressure inlet CPLI of multi-stage compression unit unit MCPU connects the low tension outlet MPLO of backheat precooling unit MRU; The high-pressure outlet MPHO of backheat precooling unit MRU connects the entrance EVI of evaporator unit EVU, and evaporator unit EVU outlet EVO connects the low-pressure inlet MPLI of backheat precooling unit MRU;
Described compound compressor unit forms (cooler that aftercooler is the afterbody compression) by a compound compressor MCP (every stage compressor CPj) and interstage cooler AFCj, and j is number of compression stages; Its connected mode is:
1) air entry of first order compressor CP1 is the low-pressure inlet CPLI of compound compressor unit MCPU, and corresponding power pressure is the 1st pressure stage;
2) first order compressor CP1 exhaust outlet connects the first interstage cooler AFCl, and the first interstage cooler AFCl exhaust outlet connects the 2nd pressure stage gas supplementing opening PMI1, then connects high stage compressor CP2 air entry, and corresponding power pressure is the 2nd pressure stage;
3) high stage compressor CP2 exhaust outlet connects the second interstage cooler AFC2, and the second interstage cooler AFC2 outlet connects the 3rd pressure stage gas supplementing opening PMI2, then connects third level compressor CP3 entrance, and corresponding power pressure is the 3rd pressure stage;
4) said process continues to carry out, n stage compressor CPn exhaust outlet connects n interstage cooler AFCn, n interstage cooler AFCn outlet connects n+1 pressure stage gas supplementing opening PMIn, then connect n+1 stage compressor CPn+1 entrance, corresponding power pressure is the n+1 pressure stage, wherein: n=1,2, ..., j-1;
5) exhaust outlet of corresponding j stage compressor CPj connects j interstage cooler AFCj, and j interstage cooler AFCj outlet is that the high-pressure exhaust CPHO of compound compressor unit, corresponding power pressure are the j+1 pressure stage.
Described backheat precooling unit MRU is by n pressure stage submodule MRUZnSeries winding consists of. Its progression n determines by compound compressor progression, i.e. n=1,2 ..., j-1. The basic structure of each pressure stage submodule MRUZn is: by a n phase separator SPZn, a n restricting element JTZnWith a n Recuperative heat exchanger HXZnForm. Its connected mode is: the j+1 pressure stage outlet of prime module connects n level phase separator SPZn entrance, n level phase separator SPZn gaseous phase outlet connects the j+1 pressure stage entrance of n Recuperative heat exchanger HXZn, and the j+1 pressure stage outlet of n Recuperative heat exchanger HXZn connects the j+1 pressure stage entrance of subordinate's submodule; N level phase separator SPZn liquid phase exports mutually and connects n restricting element entrance, the outlet of n restricting element connects n Recuperative heat exchanger HXZn n+1 pressure stage entrance, the outlet of n Recuperative heat exchanger HXZn n+1 pressure stage connects the n+1 pressure stage entrance of higher level's module Recuperative heat exchanger, finally is connected with the intermediate pressure stage gas supplementing opening MPIn+1 of compound compressor unit MCPU by intermediate pressure stage outlet PMOn+1.
Described n Recuperative heat exchanger HXZn has n+2 pressure stage passage, and comprising the cold working medium heat exchanger channels of be cooled working medium heat exchanger channels and the 1st pressure stage of j+1 pressure stage, and n the cold working medium heat exchanger channels of intermediate pressure stage forms.
Described backheat precooling unit MRU structure can also be made of n stage pressure level submodule MRUZn series winding for: backheat precooling unit MRU; Each pressure stage can also have 2 with pressure stage submodule series winding formation; These two connected modes with the pressure stage submodule are: the j+1 pressure stage of prime module is connected to the front phase separator SPZn of n pressure stage submodule1, front phase separator SPZn1Recuperative heat exchanger HXZn before gaseous phase outlet connects1J+1 pressure stage entrance, front Recuperative heat exchanger HXZn1J+1 pressure stage outlet connect after vapour liquid separator SPZn2Entrance; Front phase separator SPZn1Restricting element JTZn before liquid-phase outlet connects1Entrance, front restricting element JTZn1Heat exchanger HXZn before outlet connects1N+1 pressure stage entrance, front heat exchanger HXZn1The outlet of n+1 pressure stage connects the n+1 pressure stage entrance of prime module; Rear vapour liquid separator SPZn2Recuperative heat exchanger HXZn after gaseous phase outlet connects2J+1 pressure stage entrance, rear Recuperative heat exchanger HXZn2The outlet of n+1 pressure stage connects the n+1 pressure stage entrance of subordinate's module; Rear phase separator SPZn2Restricting element JTZn after liquid phase exports mutually and connects2Entrance, rear restricting element JTZn2Heat exchanger HXZn after outlet connects2N+1 pressure stage entrance: rear Recuperative heat exchanger HXZn2N+1 pressure stage outlet connect before Recuperative heat exchanger HXZn1N+1 pressure stage entrance, finally be connected with the intermediate pressure stage gas supplementing opening MPIn+1 of compound compressor unit MCPU by intermediate pressure stage outlet PMOn+1.
Described evaporator unit EVU comprises contra-flow heat exchanger E1, restricting element E2 and evaporimeter E3, its connected mode is: the high-pressure outlet of previous stage unit links to each other with the high pressure entry EVI of contra-flow heat exchanger E1, contra-flow heat exchanger E1 high-pressure outlet connecting joint fluid element E2 entrance, the E2 outlet connects evaporimeter E3 entrance, evaporimeter E3 outlet connects contra-flow heat exchanger E1 low-pressure inlet, and E1 low tension outlet EVO connects previous stage unit low-pressure inlet.
Therefore respectively described multiple pressure grade mixed working medium cryogenic throttling refrigeration is further characterized in that, compound compressor progression j value 2～5, corresponding 3～6 pressure stages.
Described multiple pressure grade mixed working medium cryogenic throttling refrigeration is further characterized in that, intermediate pressure progression n value is: n=1,2 ... therefore respectively, j-1, corresponding 1～4 intermediate pressure stage;
The performance of mixed working substance copious cooling refrigeration system is by determining forming of the form of the hardware of realizing refrigeration and these hardware construction systems and mixed work medium for throttling cold-producing medium. The above has set forth hardware device and the organizational form thereof that many pressure stages Refrigeration Cycle Using Refrigerant Mixture that the present invention proposes adopts, and the below forms the mixture working medium with close association of the present invention and sets forth.
Described a kind of multiple pressure grade mixed working medium cryogenic throttling refrigeration is further characterized in that the efficient multicomponent mixed working fluid that adopts with cooling flow organizational form close fit, and this mixed working fluid is comprised of 7 groups of materials, and concrete composition and concentration proportioning scope see Table 1.
Table 1 forms and concentration proportioning for the efficient mixed working fluid that the present invention adopts
| Project | Mix ingredients | Molar concentration scope % |
| The 1st group | Nitrogen (N2), argon gas (Ar) or the mixture of the two | 10～45 |
| The 2nd group | Methane (CH4), krypton (Kr) or the mixture of the two | 5～25 |
| The 3rd group | Tetrafluoromethane (CF4) | 5～20 |
| The 4th group | Ethene (C2H 4), ethane (C2H 6), fluoroform (CHF3), xenon (Xe), fluomethane (CH3F), perfluoroethylene (C2F 4), PVF (C2H 3F) or the mixture that is formed by any two form in the above-mentioned substance mixture or many kinds of substance | 5～20 |
| The 5th group | Third rare (C3H 6), propane (C3H 8), perfluoropropane (C3F 8), 1,1,1-HFC-143a (C2H 3F 3), 1,1 ,-Difluoroethane (1,1 ,-C2H 4F 2), fluoroethane (C2H 5F), allene (C3H 4), cyclopropane (C3H 6), difluoromethane (CH2F 2) or the mixture that formed by any two form in the above-mentioned substance mixture or many kinds of substance | 5～20 |
| The 6th group | 1-butylene (1-C4H 8), iso-butane (C4H 10), isopentane (C5H 12), 1-amylene (1-C5H 10), 3-methyl-1-butene (C5H 10), 2-methylpentane (C6H 14), 2-butylene (cis C4H 8), 2-butylene (trans C4H 8), cyclobutane (C4H 8), isobutene (iC4H 8), normal butane (C4H 10), perfluorinated butane (C4F 10), pentane (C5H 12), perflenapent (C5F 12) or the mixture that formed by any two form in the above-mentioned substance mixture or many kinds of substance | 5～25 |
| The 7th group | Neon (Ne)* | 0～10 |
*Adopt when only being used for realizing the following refrigeration of 80K warm area, at the above warm area of 80K, can avoid adopting.
Many pressure stages mixed work medium for throttling refrigeration system provided by the invention, have the following advantages: a plurality of pressure stages that can take full advantage of compound compressor provides improve the heat equivalent matching problem of cold fluid and hot fluid in the Recuperative heat exchanger, reduce the high low temperature of the Recuperative heat exchanger both sides heat equivalent difference that causes because of pressure differential, and then reduce the heat recovery process loss, improve the refrigeration system thermal efficiency; Can reduce again simultaneously the employing of non-condensable gas helium, neon in the system when realizing cryogenic refrigeration, the heat exchange efficiency of heat exchanger in the raising system; In addition, in many pressure stages mixed work medium for throttling refrigeration system provided by the present invention, the higher constituent element is separated in the higher temperatures district in the mixture, and return the elevated pressures level of compound compressor after its throttling, therefore only has part working medium through whole compression processes, and the higher constituent element only passes through the Partial shrinkage process, has therefore reduced the compression wasted work; Pressure reduction is maximum before and after the afterbody throttling, has guaranteed like this to have higher throttle effect at the mixed working fluid of minimum warm area throttling; The higher boiling constituent element is separated in the higher temperatures district, has reduced low-temperature space Recuperative heat exchanger conduct heat load and flowing pressure loss, avoids simultaneously the higher boiling constituent element to solidify at low temperatures and stops up restricting element, improves the reliability of refrigeration system. Another benefit that multi-stage compression brings is, reduced every grade pressure ratio, every grade of compression exhaust temperature is reduced, add simultaneously the inter-stage cooling, the compression process of system is changed near the isotherm compression process from adiabatic process, therefore reduced the loss in the compression process, show as the fire minimizing of being taken away by coolers at different levels, so overall efficiency has improved.
A kind of multiple pressure grade mixed working medium cryogenic throttling refrigeration provided by the invention, can be widely used in and satisfy various deep cooling demand occasions, such as gas liquefaction, particularly natural gas liquefaction, air separation, chemical industry tail gas liquefaction recovery, associated gas, coal gas gasification etc.; Also can be applied to cooling high-temperature superconducting device, the cooling of cold neutron source methane moderator, ultrahigh vacuum steam cold-trap etc., have extensive and important meaning.
Description of drawings
Fig. 1 refrigeration system main-process stream is arranged schematic diagram
Fig. 2 compound compressor unit and porting schematic diagram
Fig. 3 backheat precooling unit connection diagram
Two submodule series windings of Fig. 4 n pressure stage schematic diagram
Fig. 5 evaporator unit structural representation
4 one of Fig. 6 embodiment adopt 3 pressure stage mixed working substance copious cooling throttle refrigeration systems
5 one of Fig. 7 embodiment adopt 3 pressure stage mixed working substance copious cooling throttle refrigerant gas liquefaction systems
Wherein: MCPU backheat precooling unit, compound compressor unit MRU evaporator unit EVU
Compound compressor low-pressure inlet CPLI compound compressor high-pressure outlet CPHO
Backheat precooling unit high pressure entry MPHI backheat precooling unit high-pressure outlet MPHO
Backheat precooling unit low-pressure inlet MPLI backheat precooling unit low tension outlet MPLO
Recuperative heat exchanger HXZn vapour liquid separator SPZn intergrade restricting element JTZn
Backheat precooling unit intermediate pressure stage outlet PMOn backheat precooling unit submodule MRUZn
Compound compressor unit intermediate pressure stage gas supplementing opening PMIn
Each stage compressor CPjNumber of compression stages j intermediate pressure progression n, n=1 wherein, 2, ..., j-1 compressor inter-stage cooler AFCj evaporator unit high pressure entry EVI contra-flow heat exchanger E1 evaporator unit low tension outlet EVO restricting element E2 evaporimeter E3 refrigerating efficiency COP Carnot efficiency CEF (CEF=COP * (TO-Tc)/Tc * 100%) natural gas NG liquefied natural gas LNG
The specific embodiment
Below in conjunction with accompanying drawing, the course of work of the multiple pressure grade mixed working medium cryogenic throttling refrigeration that the present invention is proposed is further set forth: referring to Fig. 1～3 and Fig. 5, at first the low pressure mixed working fluid of the 1st pressure stage is by the first order air entry of compound compressor unit MCPU, be CPLI, enter the first order of compressor unit, after first order compressor CP1 compression, become the 2nd pressure stage mixture working medium, then enter the first interstage cooler AFC1 and be cooled to environment temperature, after mixing, the mixed working fluid that comes by the 2nd pressure stage gas supplementing opening PMI1 enters high stage compressor CP2 by the first interstage cooler AFC1 outlet, become the 3rd pressure stage mixture working medium after the compression, equally through after the second interstage cooler AFC2 cooling, mix with the mixed working fluid that comes by the 3rd pressure stage gas supplementing opening PMI2, then enter the next stage compression, repeat identical process, until enter the afterbody compressor, i.e. j stage compressor, after the compression of j stage compressor, become j+1 pressure stage mixed working fluid, then by j level aftercooler AFCj cooling, by compressor unit exhaust outlet CPHO, enter the next stage unit---backheat precooling unit MRU.
Enter the phase separator SPZ of j-1 level submodule backheat precooling unit submodule MRUZj-1 through the high pressure entry MPHI of backheat precooling unit MRU through the j+1 pressure stage mixed working fluid of compressor unit exhaust outlet CPHOn, being divided into two strands of working medium streams of high pressure vapor and liquid phase, the high pressure vapor fluid enters the working medium cooling of being backflowed among the Recuperative heat exchanger HXZn, then enters next pressure stage submodule, becomes the high pressure incoming flow working medium of next stage submodule; The high pressure liquid phase fluid enters intergrade restricting element JTZn, temperature reduces after the throttling, pressure becomes n level low-pressure stage, enter Recuperative heat exchanger HXZn cold is provided, then enter successively each high temperature level Recuperative heat exchanger, temperature is recovered near room temperature, and the at last PMOn intermediate pressure stage outlet by backheat precooling unit is connected with the PMIn intermediate pressure stage gas supplementing opening of compound compressor unit and enters compressor unit. High pressure incoming flow working medium is by separating step by step and cooling off, temperature and flow all reduce gradually, enter the module evaporator unit EVU of subordinate by backheat precooling unit high-pressure outlet MPHO at last, enter afterbody restricting element E2 after the further cooling through contra-flow heat exchanger E1 among the EVU, by becoming the 1st pressure stage mixed working fluid after j+1 pressure stage throttling, provide cold through evaporimeter E3; Enter backheat precooling unit MRU by evaporator unit EVU fluid out through backheat precooling unit low-pressure inlet MPLI, Recuperative heat exchanger through submodules at different levels, rewarming step by step, enter at last the low-pressure inlet CPLI of compressor unit by backheat precooling unit low tension outlet MPLO, this fluid streams has minimum pressure rating, finally finishes whole kind of refrigeration cycle. Descending by module progression, pressure stage reduced step by step after institute separated highly pressurized liquid throttling, and got back to low compression stage corresponding to compressor unit after passing through Recuperative heat exchanger rewarmings at different levels.
Every stage pressure level submodule can also have 2 with pressure stage submodule series winding formation among the backheat precooling unit MRU; Referring to Fig. 4, these two connected modes with the pressure stage submodule are: the high pressure incoming flow enters the front phase separator SPZn of n pressure stage1, be separated into high pressure vapor fluid and high pressure liquid phase fluid; The high pressure vapor fluid enters front Recuperative heat exchanger HXZn 1, obtain entering rear phase separator SPZ after the coolingn 2, again be separated into high pressure vapor fluid and high pressure liquid phase fluid, wherein the high pressure vapor fluid enters next pressure stage module; Restricting element JTZ after the high pressure liquid phase fluid process that obtains after above-mentioned rear phase separator separatesn 2Become n+1 pressure stage mixed working fluid after the throttling and enter rear heat exchanger HXZn 2Reclaim cold; The high pressure liquid phase fluid that obtains after front separator separates is through front restricting element JTZn 1Become equally n+1 level low-pressure fluid after the throttling, with process HXZn 2N+1 pressure stage low-pressure fluid behind the rewarming enters front Recuperative heat exchanger HXZ after mixingn 1Reclaim cold, then enter the upper level module.
Embodiment 1
The mixed working substance copious cooling throttle refrigeration system of 6 pressure stages of preparation is for the highly effective refrigeration of realizing the 65K warm area. This 6 stage pressure level refrigeration system is that 5 stage compressors drive. The total connected mode of this refrigeration system is referring to Fig. 1, and wherein compound compressor unit MCPU schematic diagram is referring to Fig. 2, and backheat precooling cellular construction schematic diagram is seen Fig. 3, and evaporator unit EVU structural representation is seen Fig. 5, j=5 wherein, n=j-1=4. Environment temperature 300K, multicomponent mixture work medium composition, operating pressure parameter and performance of refrigerant systems are:
| Project | The mixture constituent element | Molar concentration % |
| The 1st group | Nitrogen (N2) and the mixture of argon gas (Ar) | 35(N 2 25％、Ar 10％) |
| The 2nd group | Methane (CH4) | 5 |
| The 3rd group | Tetrafluoromethane (CF4) | 10 |
| The 4th group | Ethene (C2H 4) and fluoroform (CHF3) mixture | 10 (each 5%) |
| The 5th group | Propane (C3H 8) | 10 |
| The 6th group | Iso-butane (C4H 10) and isopentane (C5H 12) | 20 (each 10%) |
| The 7th group | Neon (Ne) | 10 |
| High voltage/low voltage (MPa) | 4.5/0.1 every grade of pressure ratio is that 2.141,6 pressure stages are respectively: 0.1 (minimal pressure), 0.2141,0.4584,9.815,2.1013,4.5 (the highest pressures at expulsion) | |
| COP | 0.106 | |
| CEF％ | 38.3 | |
The mixed working substance copious cooling throttle refrigeration system of 5 pressure stages of preparation is for the highly effective refrigeration of realizing the 80K warm area. This 5 stage pressure level refrigeration system is that 4 stage compressors drive. The total connected mode of this refrigeration system is referring to Fig. 1, and wherein compound compressor unit MCPU schematic diagram is referring to Fig. 2, and backheat precooling cellular construction schematic diagram is seen Fig. 3, and evaporator unit EVU structural representation is seen Fig. 5, j=4 wherein, n=j-1=3. Environment temperature 300K, multicomponent mixture work medium composition, operating pressure parameter and performance of refrigerant systems are:
| Project | The mixture constituent element | Molar concentration % |
| The 1st group | Nitrogen (N2) | 45 |
| The 2nd group | Methane (CH4) | 10 |
| The 3rd group | Tetrafluoromethane (CF4) | 5 |
| The 4th group | Ethane (C2H 6) and fluoroform (CHF3) mixture | 10 (each 5%) |
| The 5th group | Propane (C3H 8) | 5 |
| The 6th group | Iso-butane (C4H 10) and isopentane (C5H 12) mixture | 25 (iso-butane 15+ isopentane 10) |
| The 7th group | Neon (Ne) | 0 |
| High voltage/low voltage | 2.5/0.1 (MPa), every grade of pressure ratio is that 2.236,5 pressure stages are respectively: 0.1,0.2236,0.5,1.118,2.5 (MPa) | |
| COP | 0.169 | |
| CEF％ | 37.2 | |
Embodiment 3
The mixed working substance copious cooling throttle refrigeration system of 4 pressure stages of preparation is for the highly effective refrigeration of realizing the 90K warm area. This 4 stage pressure level refrigeration system is that 3 stage compressors drive. The total connected mode of this refrigeration system is referring to Fig. 1, and wherein compound compressor unit MCPU schematic diagram is referring to Fig. 2, and backheat precooling cellular construction schematic diagram is seen Fig. 3, and evaporator unit EVU structural representation is seen Fig. 5, j=3 wherein, n=j-1=2. Environment temperature 300K, multicomponent mixture work medium composition, operating pressure parameter and performance of refrigerant systems are:
| Project | The mixture constituent element | Molar concentration % |
| The 1st group | Nitrogen (N2) | 40 |
| The 2nd group | Krypton (Kr) | 5 |
| The 3rd group | Tetrafluoromethane (CF4) | 10 |
| The 4th group | Ethene (C2H 4) and ethane (C2H 6) | 10 (each 5%) |
| The 5th group | Propane (C3H 8) | 10 |
| The 6th group | 1-butylene (1-C4H 8), iso-butane (C4H 10), isopentane (C5H 12), 1-amylene (1-C5H 10), 3-methyl-1-butene (C5H 10), 2-methylpentane (C6H 14), 2-butylene (cis C4H 8), 2-butylene (trans C4H 8), cyclobutane (C4H 8), isobutene (iC4H 8), normal butane (C4H 10), perfluorinated butane (C4F 10), pentane (C5H 12), perflenapent (C5F 12) mixture that forms | 25, wherein iso-butane 12, all the other each 1%. |
| The 7th group | Neon (Ne) | 0 |
| High voltage/low voltage | 2.5/0.1 (MPa), every grade of pressure ratio is that 2.924,4 pressure stages are respectively: 0.1,0.2924,0.855,25 (MPa) | |
| COP | 0.186 | |
| CEF％ | 43.4 | |
Embodiment 4
The mixed working substance copious cooling throttle refrigeration system of 3 pressure stages of preparation is for the highly effective refrigeration of realizing the 100K warm area. This 3 stage pressure level refrigeration system is that 2 stage compressors drive. The total connected mode of this refrigeration system is referring to Fig. 1, wherein compound compressor unit MCPU schematic diagram is referring to Fig. 2, backheat precooling cellular construction schematic diagram is seen Fig. 3 and Fig. 4, evaporator unit EVU structural representation is seen Fig. 5, j=2 wherein, n=j-1=1, namely in the middle of backheat precooling unit only have a pressure to separate level, but adopt two to separate level (concrete organization chart is referring to a Fig. 4). Separate refrigeration system for further clearly demonstrating these 3 pressure stage mixed working fluids, Fig. 6 has provided the refrigeration system schematic diagram. Environment temperature 300K, multicomponent mixture work medium composition, operating pressure parameter and performance of refrigerant systems are:
| Project | The mixture constituent element | Molar concentration % |
| The 1st group | Nitrogen (N2) and the mixture of argon gas (Ar) | 35,25 (N wherein2)+10(Ar) |
| The 2nd group | Methane (CH4) | 10 |
| The 3rd group | Tetrafluoromethane (CF4) | 5 |
| The 4th group | Ethene (C2H 4), ethane (C2H 6), fluoroform (CHF3), xenon (Xe), fluomethane (CH3F), perfluoroethylene (C2F 4), PVF (C2H 3F) mixture that forms | 20, ethane (C wherein2H 6) 2%, all the other are 3% years old |
| The 5th group | Propane (C3H 8) | 5 |
| The 6th group | Iso-butane (C4H 10)+isopentane (C5H 12) | 25 (iso-butane 15+ isopentane 10) |
| The 7th group | Neon (Ne) | 0 |
| High voltage/low voltage | 2.4/0.15 (MPa), every grade of pressure ratio is that 4,3 pressure stages are respectively: 0.15,0.6,2.4 (MPa) | |
| COP | 0.185 | |
| CEF％ | 37 | |
Embodiment 5
The mixed working substance copious cooling throttle refrigeration system of 3 pressure stages of preparation is for the highly effective refrigeration of realizing the 110K warm area. This 3 stage pressure level refrigeration system is that 2 stage compressors drive. The total connected mode of this refrigeration system is referring to Fig. 1, and wherein compound compressor unit MCPU schematic diagram is referring to Fig. 2, and backheat precooling cellular construction schematic diagram is seen Fig. 3, and evaporator unit EVU structural representation is seen Fig. 5, j=2 wherein, n=j-1=1. Environment temperature 300K, multicomponent mixture work medium composition, operating pressure parameter and performance of refrigerant systems are:
| Project | The mixture constituent element | Molar concentration % |
| The 1st group | Haidian District, Beijing 100080 2 North a...2Haidian District, Beijing 100080 2 North a... | 30, where 20 (N2)+10(Ar) |
| 30, where 20 (N... | 30, where 20 (N...4) | 25 |
| Group 3 | Tetrafluoride (CF4) | 15 |
| Group 4 | Ethylene (C2H 4) | 5 |
| Group 5 | Group 5...3H 6Group 5...3H 8), Perfluoro propane (C3F 8), 1,1,1 - trifluoro-ethane (C2H 3F 3), 1,1,1 - trifluoro-ethane (C...2H 4F 2), 1,1,1 - trifluoro-ethane (C...2H 5F), allene (C3H 4), Cyclopropane (C3H 6), Difluoromethane (CH2F 2) A mixture consisting of | 20, wherein the propane (C3H 8) 4%, and the remaining Each 2% |
| Group 6 | Isopentane (C5H 12) | 5 |
| Seventh group | Neon (Ne) | 0 |
| High / low pressure | 2.4/0.15 (MPa), pressure ratio per stage 4,3 pressure stages were: 0.15,0.6,2.4 (MPa) | |
| COP | 0.216 | |
| CEF％ | 37.3 | |
Example 6
Preparation of a three-level mixed refrigerant pressure cryogenic refrigeration system throttling for the realization of liquefied natural gas (minimum
Refrigeration temperature 110 ~ 120K temperature zone). The three pressure stage compressor refrigeration system for the two drivers. The refrigeration system
Total Connection Referring to Figure 1, multi-stage compressor unit MCPU diagram shown in Figure 2, the heat pre-cooling unit Results
Configuration is shown in Figure 3 and Figure 4, the evaporator unit EVU structure diagram in Figure 5, where j = 2, n = j-1 = 1, i.e.
Intermediate regenerator pre-cooling unit is only one pressure stage, but using two separation stages (org chart specifically see Figure 4).
To further clear that the pressure level of the three separate cooling system refrigerant mixtures, Figure 7 shows the schematic diagram of the refrigeration system.
Ambient temperature 300K, multivariate mixed refrigerant composition, operating pressure and cooling system performance parameters as follows:
...
| Preparation of a three-level mixed refrigerant pressure cryogenic refrigeration system throttling for the realization of liquefied natural gas (minimum Refrigeration temperature 110 ~ 120K temperature zone). The three pressure stage compressor refrigeration system for the two drivers. The refrigeration system Total Connection Referring to Figure 1, multi-stage compressor unit MCPU diagram shown in Figure 2, the heat pre-cooling unit Results Configuration is shown in Figure 3 and Figure 4, the evaporator unit EVU structure diagram in Figure 5, where j = 2, n = j-1 = 1, i.e. Intermediate regenerator pre-cooling unit is only one pressure stage, but using two separation stages (org chart specifically see Figure 4). To further clear that the pressure level of the three separate cooling system refrigerant mixtures, Figure 7 shows the schematic diagram of the refrigeration system. Ambient temperature 300K, multivariate mixed refrigerant composition, operating pressure and cooling system performance parameters as follows: ... | Mixture component | Molar concentration% |
| Group 1 | Nitrogen (N2) | 25 |
| |
Methane (CH4) | 25 |
| Group 3 | Tetrafluoride (CF4) | 10 |
| Group 4 | Ethane (C2H 6) | 10 |
| Group 5 | Propane (C3H 8) | 15 |
| Group 6 | Isobutane (C4H 10Isobutane (C...5H 12) | Isobutane (C... |
| Seventh group | Neon (Ne) | 0 |
| High / low pressure | 2.4/0.15 (MPa), pressure ratio per stage 4,3 pressure stages were: 0.15,0.6,2.4 (MPa) | |
| Than the power | 2.178 liters LNG / kw.h | |
| CEF％ | 35.6 | |
Claims (9)
1, a multi-level mixed refrigerant pressure throttling cryogenic refrigeration system, wherein: the multi-stage compressor single
Yuan (MCPU), pre-cooling heat recovery unit (MRU) and the evaporator unit (EVU) composition; its connection to: multi-stage compression
Unit cell (MCPU) high-pressure outlet (CPHO) to connect back hot pre-cooling unit (MRU) high-pressure inlet (MPHI), multi-
Stage compressor unit (MCPU) low pressure inlet (CPLI) to connect back to heat pre-cooling unit (MRU) of the low-pressure outlet
(MPLO); regenerator pre-cooling unit (MRU) of the high pressure outlet (MPHO) connector evaporator unit (EVU) inlet
(EVI), evaporator unit (EVU) exit (EVO) to connect back to heat pre-cooling unit (MRU) of the low-pressure inlet (MPLI);
The multi-stage compressor unit consists of a multi-stage compressor, each level is (CPj), and an interstage cooler (AFCj)
Composition, j is the compression stages; its connection to:
1) a first stage compressor (CP1) of the intake port of multi-stage compressor unit (MCPU) of the low-pressure inlet (CPLI), the
Should be working fluid pressure of the first pressure stage;
2) The first stage compressor (CP1) exhaust port connected to the first inter-stage cooler (AFC1), the first inter-stage cooler (AFC1)
Exhaust port connecting the second pressure stage qi mouth (PMI1), then connect the second stage compressor (CP2) intake port, the corresponding working fluid
Pressure of the second pressure level;
3) The second stage compressor (CP2) exhaust port connected to the second inter-stage cooler (AFC2), the second inter-stage cooler (AFC2)
Outlet Connection 3 pressure stages qi mouth (PMI2), then connect the third stage compressor (CP3) entry, the corresponding working fluid pressure
For the first three pressure level;
4) continuing the above process, the n-stage compressor (CPn) connected to an exhaust port between the n-stage cooler (AFCn),
N-th inter-stage cooler (AFCn) outlet pressure level (n +1) qi mouth (PMIn), then connect the (n +1)-level pressure
Compressor (CPn +1) entry, corresponding to a pressure of the working fluid pressure level (n +1), where: n = 1,2, ..., j-1;
5) corresponding to the j-th stage compressor (CPj) connecting the exhaust port of the j-th inter-stage cooler (AFCj), the j-th inter-stage cooler
(AFCj) outlet of the compressor unit is multistage high-pressure exhaust port (CPHO), corresponding to the working fluid pressure of the first pressure stage j +1;
The pre-cooling heat recovery unit (MRU) pressure level consists of n sub-module (MRUZn) concatenated form; their order n by the
Decision multistage compressor stages, i.e. n = 1,2 ..., j-1; the pressure-level sub-module (MRUZn) the basic structure:
By an n-th vapor phase separator (SPZn), one of the first throttling element n (JTZn) and a heat exchanger back to the n
(HXZn) components. Its connection to: the former first j +1 level modules connected to the outlet pressure of the n-th stage vapor-liquid separator
(SPZn) entry, the n-th stage vapor-liquid separator (SPZn) gas outlet connected n-regenerator heat exchanger (HXZn) the first j +1
Pressure stage entrance, the n-back heat exchanger (HXZn) the first j +1 outlet pressure stage the first lower sub-module j +1 pressure
Force-level entrance; n-th stage vapor-liquid separator (SPZn) liquid phase outlet connecting the first inlet throttling element n, n-throttle
Components connected to the outlet of the heat recovery heat exchanger n (HXZn) (n +1) pressure stage entrance, the n-back heat exchanger (HXZn) Section
n +1 higher pressure stage outlet heat exchanger module back to the (n +1) pressure stage entrance, and ultimately through the intermediate pressure
Stage outlet (PMOn +1) the multi-stage compressor unit (MCPU) of the intermediate pressure stage qi port (MPIn +1) connections;
...
The pre-cooling heat recovery unit (MRU) pressure level consists of n sub-module (MRUZn) concatenated form; their order n by the
Decision multistage compressor stages, i.e. n = 1,2 ..., j-1; the pressure-level sub-module (MRUZn) the basic structure:
By an n-th vapor phase separator (SPZn), one of the first throttling element n (JTZn) and a heat exchanger back to the n
(HXZn) components. Its connection to: the former first j +1 level modules connected to the outlet pressure of the n-th stage vapor-liquid separator
(SPZn) entry, the n-th stage vapor-liquid separator (SPZn) gas outlet connected n-regenerator heat exchanger (HXZn) the first j +1
Pressure stage entrance, the n-back heat exchanger (HXZn) the first j +1 outlet pressure stage the first lower sub-module j +1 pressure
Force-level entrance; n-th stage vapor-liquid separator (SPZn) liquid phase outlet connecting the first inlet throttling element n, n-throttle
Components connected to the outlet of the heat recovery heat exchanger n (HXZn) (n +1) pressure stage entrance, the n-back heat exchanger (HXZn) Section
n +1 higher pressure stage outlet heat exchanger module back to the (n +1) pressure stage entrance, and ultimately through the intermediate pressure
Stage outlet (PMOn +1) the multi-stage compressor unit (MCPU) of the intermediate pressure stage qi port (MPIn +1) connections;
...
2, according to claim 1, wherein a multi-stage mixed refrigerant pressure throttling cryogenic refrigeration system characterized in that:
The pre-cooling heat recovery unit (MRU) structure: pre-cooling heat recovery unit (MRU) consists of n-level sub-module level pressure
(MRUZn) concatenated form; each pressure level can also have two sub-modules in series with the pressure level constituted; these two different pressure
Force-level sub-module connections: the former first j 1 level modules connected to the n-level pressure pressure stage steam before submodules
Phase separator (SPZn1), The first vapor-liquid separator (SPZn1) Gas outlet heat exchanger before connecting back (HXZn1) First
j +1 pressure stage entrance, heat exchanger frontal gyrus (HXZn1) J +1 of the first stage outlet pressure vapor-liquid separator is connected (SPZn2)
Entrance; former vapor-liquid separator (SPZn1) Before connecting the liquid outlet throttling element (JTZn1) Entrance, before throttling element
(JTZn1) Before connecting the heat exchanger outlet (HXZn1) (N +1) pressure stage entrance, the front heat exchanger (HXZn1) (N +1)
Outlet pressure stage preamp module inlet pressure stage (n +1); after vapor-liquid separator (SPZn2) (N +1)
Outlet pressure stage preamp module inlet pressure stage (n +1); after vapor-liquid separator (SPZn...2) (N +1)
Outlet pressure stage preamp module inlet pressure stage (n +1); after vapor-liquid separator (SPZn...2) First pressure stage exit n 1
The first module is connected to the lower pressure stage n 1 entrance; After the vapor-liquid separator (SPZn2) Liquid phase outlet connection throttling
Component (JTZn2) Entrance, after throttling element (JTZn2) After the heat exchanger outlet connection (HXZn2) After the heat exchanger outlet connection (HXZn...2) After the heat exchanger outlet connection (HXZn...1) A first n 1
Inlet pressure stage, and ultimately through the intermediate pressure stage outlet (PMOn 1) the multi-stage compressor unit (MCPU) of the intermediate pressure
Force levels qi mouth (MPIn 1) connection.
3, according to claim 1 or 2, wherein a multi-stage mixed refrigerant pressure throttling cryogenic refrigeration system, characterized by
Further characterized by: said first heat exchanger back to n (HXZn) has a pressure stage n +2 channels, including the first pressure j +1
Level working fluid is cooled and the first heat exchange passage pressure stage cold heat exchanger working fluid channel, and n intermediate pressure stage cold work
Quality Heat channels.
4, according to claim 1 or 2, wherein a multi-stage mixed refrigerant pressure throttling cryogenic refrigeration system, characterized by
Further characterized by: a multistage compressor stages j ranging from 2 to 5, thus corresponding to the pressure stages 3-6.
5, according to claim 3 wherein a multi-stage mixed refrigerant pressure throttling cryogenic refrigeration system, further characterized in that
In: multi-stage compressor stages j ranging from 2 to 5, thus corresponding to the pressure stages 3-6.
6, according to claim 1 or 2, wherein a multi-stage mixed refrigerant pressure throttling cryogenic refrigeration system, characterized by
Further characterized by: an intermediate pressure value of order n: n = 1,2 ..., j-1, so 1 to 4, which correspond to intermediate pressure stage.
7, according to claim 3 wherein a multi-stage mixed refrigerant pressure throttling cryogenic refrigeration system, further characterized in that
On: intermediate pressure value of order n: n = 1,2 ..., j-1, so each of 1 to 4 corresponding to the intermediate pressure level.
8, according to claim 4, wherein the pressure of a multi-stage mixed refrigerant throttling cryogenic refrigeration system, further characterized in that
On: intermediate pressure value of order n: n = 1,2 ..., j-1, so each of 1 to 4 corresponding to the intermediate pressure level.
9, according to claim 1, wherein a multi-stage mixed refrigerant pressure throttling cryogenic refrigeration system, further characterized in that
Adopt and cooling processes in close cooperation and efficient organizational forms multivariate mixed refrigerant, the refrigerant mixtures composed of seven groups of substances set
A specific composition and concentration ratio ranges:
Group 1: nitrogen, argon or a mixture thereof, the molar concentration range of 10 to 45%;
Group 2: alkyl, krypton or a mixture thereof, the molar concentration range of 5-25%;
Group 3: Tetrafluoromethane, the molar concentration range of 5 ~ 20%;
Group 4: ethylene, ethane, trifluoromethane, xenon, fluoro methane, perfluoro vinyl fluoride or by the
Any two of said substances in a mixture consisting of; or by the material mixture consisting of a variety of
Matter, the molar concentration range of 5 ~ 20%;
Group 4: ethylene, ethane, trifluoromethane, xenon, fluoro methane, perfluoro vinyl fluoride or by the
Any two of said substances in a mixture consisting of; or by the material mixture consisting of a variety of
Matter, the molar concentration range of 5 ~ 20%;...
Group 4: ethylene, ethane, trifluoromethane, xenon, fluoro methane, perfluoro vinyl fluoride or by the
Any two of said substances in a mixture consisting of; or by the material mixture consisting of a variety of
Matter, the molar concentration range of 5 ~ 20%;...4H
8) 2 - butene (trans-C
...4H
8) 2 - butene (trans-C
...
Group 7: neon gas, the molar concentration range of 0 to 10%.
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| CN101617182B (en) * | 2007-02-26 | 2012-01-04 | 开利公司 | Economized refrigerant system utilizing expander with intermediate pressure port |
| CN102331103A (en) * | 2011-03-15 | 2012-01-25 | 中科赛凌（北京）科技有限公司 | Method for adjusting and controlling capability and work condition of cryogenic mixed working medium throttling refrigeration system |
| CN102494467A (en) * | 2011-12-07 | 2012-06-13 | 中科赛凌（北京）科技有限公司 | Throttling and refrigerating freezing storage box with two-stage fractional condensation and separation reheating type mixed working medium |
| CN102618220A (en) * | 2011-01-26 | 2012-08-01 | 龙志刚 | Mixed refrigerant suitable for 120-150K cryogenic temperature region |
| CN102719226A (en) * | 2012-06-19 | 2012-10-10 | 中国科学院理化技术研究所 | Multi-element mixed refrigerant suitable for cryogenic temperature zone of-130 to-180 DEG C |
| CN102840705A (en) * | 2012-09-10 | 2012-12-26 | 中国科学院理化技术研究所 | Deep cooling mixed working medium throttling refrigeration system |
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| CN105823300A (en) * | 2015-01-06 | 2016-08-03 | 中国石化工程建设有限公司 | Low-energy consumption natural gas liquefaction method |
| CN107514871A (en) * | 2016-06-17 | 2017-12-26 | 中国石化工程建设有限公司 | Single compressor azeotrope natural gas liquefaction system and method |
| CN108489133A (en) * | 2018-03-13 | 2018-09-04 | 中国科学院理化技术研究所 | Multi-stage compression mixed working medium refrigerating/liquefying system |
| CN108613478A (en) * | 2018-05-15 | 2018-10-02 | 中国石油工程建设有限公司 | A kind of extremely cold area natural gas liquefaction device and method |
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| CN101617182B (en) * | 2007-02-26 | 2012-01-04 | 开利公司 | Economized refrigerant system utilizing expander with intermediate pressure port |
| CN102618220B (en) * | 2011-01-26 | 2016-06-15 | 龙志刚 | A kind of mix refrigerant being applicable to 120K～150K Shen Lengwen district |
| CN102618220A (en) * | 2011-01-26 | 2012-08-01 | 龙志刚 | Mixed refrigerant suitable for 120-150K cryogenic temperature region |
| CN102331103A (en) * | 2011-03-15 | 2012-01-25 | 中科赛凌（北京）科技有限公司 | Method for adjusting and controlling capability and work condition of cryogenic mixed working medium throttling refrigeration system |
| CN102494467A (en) * | 2011-12-07 | 2012-06-13 | 中科赛凌（北京）科技有限公司 | Throttling and refrigerating freezing storage box with two-stage fractional condensation and separation reheating type mixed working medium |
| CN102719226A (en) * | 2012-06-19 | 2012-10-10 | 中国科学院理化技术研究所 | Multi-element mixed refrigerant suitable for cryogenic temperature zone of-130 to-180 DEG C |
| CN102719226B (en) * | 2012-06-19 | 2015-10-07 | 中国科学院理化技术研究所 | Multi-element mixed refrigerant suitable for cryogenic temperature zone of-130 to-180 DEG C |
| CN102840705A (en) * | 2012-09-10 | 2012-12-26 | 中国科学院理化技术研究所 | Deep cooling mixed working medium throttling refrigeration system |
| CN105823300A (en) * | 2015-01-06 | 2016-08-03 | 中国石化工程建设有限公司 | Low-energy consumption natural gas liquefaction method |
| CN105571187A (en) * | 2016-01-04 | 2016-05-11 | 上海理工大学 | Ultralow-temperature cascade refrigerating system adopting Xe as low-temperature stage refrigerant |
| CN107514871A (en) * | 2016-06-17 | 2017-12-26 | 中国石化工程建设有限公司 | Single compressor azeotrope natural gas liquefaction system and method |
| CN108489133A (en) * | 2018-03-13 | 2018-09-04 | 中国科学院理化技术研究所 | Multi-stage compression mixed working medium refrigerating/liquefying system |
| CN108489133B (en) * | 2018-03-13 | 2023-10-20 | 中国科学院理化技术研究所 | Multi-stage compression mixed working medium refrigerating/liquefying system |
| CN108613478A (en) * | 2018-05-15 | 2018-10-02 | 中国石油工程建设有限公司 | A kind of extremely cold area natural gas liquefaction device and method |
| CN113701387A (en) * | 2021-04-07 | 2021-11-26 | 中国科学院理化技术研究所 | Supersonic two-phase expansion multi-stage low-temperature refrigeration system and refrigerator |
| CN113701387B (en) * | 2021-04-07 | 2022-10-28 | 中国科学院理化技术研究所 | Supersonic two-phase expansion multistage low-temperature refrigerating system and refrigerator |
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