[go: up one dir, main page]

US3396784A - Honeycomed restricted tube heat exchanger - Google Patents

Honeycomed restricted tube heat exchanger Download PDF

Info

Publication number
US3396784A
US3396784A US541357A US54135766A US3396784A US 3396784 A US3396784 A US 3396784A US 541357 A US541357 A US 541357A US 54135766 A US54135766 A US 54135766A US 3396784 A US3396784 A US 3396784A
Authority
US
United States
Prior art keywords
gas
tubes
exchanger
heat exchanger
spaces
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US541357A
Other languages
English (en)
Inventor
Ergenc Mehmet Sahabettin
Liem Tjing Hian
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sulzer AG
Original Assignee
Sulzer AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sulzer AG filed Critical Sulzer AG
Application granted granted Critical
Publication of US3396784A publication Critical patent/US3396784A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • 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
    • F25J1/0005—Light or noble gases
    • F25J1/001—Hydrogen
    • 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
    • F25J1/0005—Light or noble gases
    • F25J1/0007—Helium
    • 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
    • F25J1/0032—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 the feed stream itself or separated fractions from it, i.e. "internal refrigeration"
    • F25J1/0035—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 the feed stream itself or separated fractions from it, i.e. "internal refrigeration" by gas expansion with extraction of work
    • F25J1/0037—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 the feed stream itself or separated fractions from it, i.e. "internal refrigeration" by gas expansion with extraction of work of a return stream
    • 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
    • F25J1/0032—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 the feed stream itself or separated fractions from it, i.e. "internal refrigeration"
    • F25J1/004—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 the feed stream itself or separated fractions from it, i.e. "internal refrigeration" by flash gas recovery
    • 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
    • F25J1/0201—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 only internal refrigeration means, i.e. without external refrigeration
    • F25J1/0202—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 only internal refrigeration means, i.e. without external refrigeration in a quasi-closed internal refrigeration loop
    • 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
    • F25J5/00—Arrangements of cold exchangers or cold accumulators in separation or liquefaction plants
    • F25J5/002—Arrangements of cold exchangers or cold accumulators in separation or liquefaction plants for continuously recuperating cold, i.e. in a so-called recuperative heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0041—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for only one medium being tubes having parts touching each other or tubes assembled in panel form
    • 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
    • F25J2270/04—Internal refrigeration with work-producing gas expansion loop
    • F25J2270/06—Internal refrigeration with work-producing gas expansion loop with multiple gas expansion loops
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S62/00—Refrigeration
    • Y10S62/902—Apparatus
    • Y10S62/903—Heat exchange structure

Definitions

  • the exchanger .of the invention comprises, for traversal by the low pressure cooling gas, a plurality of tubes of circular cross-section extending parallel to and in contact with each other in a honeycomb, inside a jacket of polygonal cross-section which contacts the outermost tubes of the honeycomb.
  • the spaces of substantially triangular cross-section between adjacent tubes of the honeycomb and between the jacket and the outermost tubes of the honeycomb constitute channels which are traversed by the gas at high pressure to be cooled, and the tubes have a constriction at one point along their length inside the jacket to permit cross-flow among those channels of substantially triangular cross-section.
  • the present invention relates to low temperature cooling apparatus for cooling a gas of low boiling point such as hydrogen or helium to very low temperature, and preferably for liquefying it, in which the gas is compressed to high pressure, is then cooled below its inversion temperature, and then before being expanded in a throttling valve is further cooled in at least one heat exchanger by heat exchange with gas at low pressure flowing countercurrent therewith.
  • a gas of low boiling point such as hydrogen or helium
  • the gas to be cooled such as helium or hydrogen
  • the gas to be cooled is expanded through a throttling valve for achievement of the desired cooling effect at the very low temperatures in question.
  • the gas so expanded is cooled because of the positive nature of the Joule-Thomson effect at these low temperatures, and it may be partly liquefied as well.
  • the compressed gas is first cooled to a preliminary cooling temperature hereinafter denoted T below its inversion temperature, as for example by expansion with performance of external work or by heat exchange with external refrigerants. It is then further cooled by countercurrent flow in heat exchange relation with a cooling medium expanded to a low pressure, for example the liquefaction pressure of the gas to be liquefied, before being expanded through a throttling valve.
  • T preliminary cooling temperature
  • a cooling medium expanded to a low pressure for example the liquefaction pressure of the gas to be liquefied
  • the enthalpy difference between'the gas at low pressure and that at high pressure at the preliminary cooling temperature T i.e., at the temperature prevailing at the hot end of the heat exchanger be positive.
  • the magnitude of the enthalpy difference is a measure of the avail- 3,396,784 Patented Aug. 13, 1968 ice able useful cooling effect. In gases of low boiling point however such a positive enthalpy difference is achieved at these temperatures only if the temperature diiference between the gases at high and low pressure is small.
  • Temperature differences of as little as the order of 1 at the hot end of the heat exchanger may cause the Joule- Thomson effect in the throttling step to become negative, which will produce a heating rather than a cooling of the gas desired to be cooled.
  • the specific enthalpy i of the high pressure gas is 117.12 joules per gram and degree. While the specific enthalpy i of helium as the low pressure gas at a pressure of 1 atmosphere absolute and at 21 K.
  • the invention is based upon recognition of the fact that this requirement can be met with an acceptable cost of construction if precautions are taken to provide a uniform mass distribution or density of flow over the crosssection of the heat exchanger in respect of the heat exchange surfaces.
  • heat exchangers in which one of the media involved in the heat exchange passes through a small number of parallel tubes in contact with each other, while the other medium flows through the spaces between these contiguous tubes and through the spaces between the outermost of these tubes and a jacket tube of circularly cylindrical shape which surrounds them and contacts those outermost tubes.
  • Heat exchangers of this kind are easy to construct, but they are not satisfactory, for operation with the small temperature dilferences between the two media required in low temperature systems, because of the wide disparity of rate of flow of the one medium over the cross-section of the complete exchanger.
  • a plurality of circular tubes of the same crosssection for conduction of the gas at low pressure which are parallel to each other and which touch each other longitudinally, i.e., along elements or generatrices of their circularly cylindrical shape, and these tubes are formed into a nest or bundle enclosed by a jacket tube of polygonal cross-section which touches the outermost tubes of the bundle along a generatrix of each.
  • the spaces of approximately triangular cross-section between the small tubes and between the outermost thereof and the jacket tube serve for passage of the gas at high pressure.
  • the cross-section for flow of the low pressure gas i.e., the aggregate of the cross-sections of the small tubes
  • the cross-section for flow of the high pressure gas is made up of the spaces between the individual tubesas distinguished from the space between the outer tubes of the bundle and the surrounding jacket.
  • the heat exchanger of the invention has a relatively long length, for instance the tube length is at least five hundred times the diameter of the individual tubes, relatively high streaming speeds of the media and large heat transfer values being thereby obtained based on the relative small cross-section of the heat exchanger.
  • the relatively large temperature difference between the two media at the cold end of the exchanger compared to the relaitvely small temperature difference at the hot end, is specified by the requirements of the process to be carried out in the low temperature system in which the exchanger is es ecially intended to be used.
  • a relatively low preliminary cooling temperature that of the high pressure gas upon entry into the exchanger
  • This is a consequence of the relatively large throttling undergone by the high pressure gas in the exchanger, and is consistent with the entropy diagrams of gases of low boiling point.
  • the invention consequently has a number of advantages.
  • the invention is characterized by an additional feature according to which for suppression of possible temperature differences among the partial streams passing through the intermediate spaces, the tubes exhibit at least once along their length a constriction in cross-section.
  • These mixing spaces can be distributed at various positions along the length of the heat exchanger.
  • FIG. 1 is a diagram of a low temperature system such as may be employed for the liquefaction of helium
  • FIG. 2 is a view in elevation, partly in section, of a heat exchanger according to the invention.
  • FIG. 3 is a sectional view taken on the line II-II in FIG. 2 shown however at an enlarged scale;
  • FIG. 4 is a further fragmentary view of the heat exchanger of FIG. 2;
  • reference character 1 identifies a heat exchanger according to the invention upstream of a throttling valve 2 in which the gas to be cooled or liquefied, e.g., helium, is expanded down to its liquefaction pressure.
  • the gas to be cooled is introduced into the system through the line 3 and is compressed in the compressor 4.
  • This gas, flowing downwardly at the left in FIG. 1, is then cooled in the heat exchangers 5, 6 and 7 by heat exchange with gas at low temperature flowing upwardly at the right in FIG. 1. It is additionally cooled by expansion with performance of external work by the flow of a part of the stream through two expansion turbines 8 and 9, the gas flowing through these turbines also passing through these exchangers 5, 6 and 7.
  • the gas is cooled down to a preliminary cooling temperature T below its inverison temperature.
  • the gas at high pressure passes downwardly (in FIG. 1) in heat exchange relation with gas at low temperature obtained as the non-liquefied fraction of the high pressure gas expanded through throttling valve 2 and/ or from liquefied gas which has been revaporized, this gas at low temperature which serves to absorb heat being withdrawn from the vapor space of a container 10.
  • the heat exchanger shown in FIG. 2 comprises a pressure resistant exterior or jacket tube 11 having a hexagonal cross-section as indicated in FIG. 3.
  • the jacket 11 encloses sixty-one tubes 12 which may be made for example of aluminum or copper.
  • end pieces 13 and 14 which may advantageously include conical portions joined by a cylinder to which connecting tubes 15 and 16 are provided for the supply and withdrawal of the gas at high pressure.
  • the gas at high pressure to be cooled flows through the intermediate spaces 17 (FIG. 3) between the tubes 12 and through the intermediate spaces 18 between the outermost tubes 12 of the nest or bundle and the surrounding jacket tube 11.
  • the tubes 12 are splayed out in conical fashion within the end vessels 13 and 14 to provide junction or mixing spaces 19 for the intermediate spaces 17 and 18 and to permit flow from and to those spaces 17 and 18 and the supply and withdrawal conduits 15 and 16.
  • the tubes 12, which in the non-limitative exemplary use of the invention described are traversed by the gas at low pressure in the opposite direction from that in which the spaces 17 and 18 are traversed, open at the opposite ends of the exchanger through isolating Walls, of which one is shown at 21, into a collection space of which one is indicated at the upper end of the exchanger in FIG. 2 by the reference character 20.
  • the Wall 21 provides a gas-tight separation between the spaces 19 and 20.
  • Connections 22 and 23 are provided to the tube spaces 20 for supply and withdrawal of low pressure gas to and from the exchanger.
  • a constriction is provided in the tubes 12 at least one point located between the ends of the jacket tube. This is indicated in FIG. 4.
  • FIG. 4 shows three of the inner tubes 12 all having a constriction 24 at the same position lengthwise thereof. At the location of these constrictions there is thus provided an interconnection, as indicated at 25, among all of the intermediate spaces 17 which assists in suppressing the development of temperature differences among the streams of gas flowing through these spaces 17.
  • the ends of the tubes 12 may likewise be provided with constrictions inside the spaces 19, i.e., prior to their passage through the separating walls 20 at the upper and lower ends of the exchanger. In such a construction therefore the splaying out of the tubes illustrated at the upper end of FIG. 2 may be dispensed with.
  • the heat exchanger of the invention possesses a hexagonal cross-section as indicated in FIG. 3.
  • the cross-section of flow for the high pressure gas provided in the spaces 17 between adjacent tubes 12 will be large compared to that provided by the spaces 18 between the outer limits of the bundle and the jacket 11.
  • the intermediate spaces 18 between the tubes 12 and the surrounding shroud can be further reduced by the insertion of blocking elements such as longitudinally extending wires.
  • the heat exchanger of the invention has been described in terms of its application to heat exchange between a gas at high pressure and a low pressure gas throttled to a particular pressure, the invention finds application also in cases where for example the high pressure gas is throttled at two valves downstream of the heat exchanger. In such a case the partial stream of gas at low pressure obtained after the first throttling passes through one fraction of the heat exchanger tubes whereas that obtained from the second throttling pass through the others.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Separation By Low-Temperature Treatments (AREA)
US541357A 1965-04-17 1966-04-08 Honeycomed restricted tube heat exchanger Expired - Lifetime US3396784A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DES0096613 1965-04-17

Publications (1)

Publication Number Publication Date
US3396784A true US3396784A (en) 1968-08-13

Family

ID=7520189

Family Applications (1)

Application Number Title Priority Date Filing Date
US541357A Expired - Lifetime US3396784A (en) 1965-04-17 1966-04-08 Honeycomed restricted tube heat exchanger

Country Status (4)

Country Link
US (1) US3396784A (de)
CH (1) CH451214A (de)
FR (1) FR1471427A (de)
GB (1) GB1135018A (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2430161A1 (de) * 1974-06-24 1976-01-15 Hochtemperatur Reaktorbau Gmbh Waermeaustauscher mit kreisfoermigem oder hexagonalem querschnitt
US3992167A (en) * 1975-04-02 1976-11-16 Union Carbide Corporation Low temperature refrigeration process for helium or hydrogen mixtures using mixed refrigerant
CN115854651A (zh) * 2022-11-25 2023-03-28 浙江大学 一种利用制冷机预冷的氢液化方法及装置

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4689962A (en) * 1986-01-17 1987-09-01 The Boc Group, Inc. Process and apparatus for handling a vaporized gaseous stream of a cryogenic liquid
GB2312495A (en) * 1996-04-25 1997-10-29 Micklewright Charles Anthony Combined condenser and heat exchanger unit

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2139367A (en) * 1935-11-20 1938-12-06 Curtiss Wright Corp Radiator core construction
US2223622A (en) * 1939-08-15 1940-12-03 Detroit Harvester Co Trim fastener
US2453737A (en) * 1944-12-11 1948-11-16 Worth Weldon Oil temperature control unit
US2466684A (en) * 1945-04-18 1949-04-12 Harold W Case Radiator core
US2532288A (en) * 1946-06-21 1950-12-05 Hydrocarbon Research Inc Heat exchange unit
US2641450A (en) * 1946-10-19 1953-06-09 Hydrocarbon Research Inc Method of transferring heat by a powdered thermophore in a state of dense phase fluidization
US3094390A (en) * 1958-07-09 1963-06-18 Air Prod & Chem Production and storage of converted hydrogen

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2139367A (en) * 1935-11-20 1938-12-06 Curtiss Wright Corp Radiator core construction
US2223622A (en) * 1939-08-15 1940-12-03 Detroit Harvester Co Trim fastener
US2453737A (en) * 1944-12-11 1948-11-16 Worth Weldon Oil temperature control unit
US2466684A (en) * 1945-04-18 1949-04-12 Harold W Case Radiator core
US2532288A (en) * 1946-06-21 1950-12-05 Hydrocarbon Research Inc Heat exchange unit
US2641450A (en) * 1946-10-19 1953-06-09 Hydrocarbon Research Inc Method of transferring heat by a powdered thermophore in a state of dense phase fluidization
US3094390A (en) * 1958-07-09 1963-06-18 Air Prod & Chem Production and storage of converted hydrogen

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2430161A1 (de) * 1974-06-24 1976-01-15 Hochtemperatur Reaktorbau Gmbh Waermeaustauscher mit kreisfoermigem oder hexagonalem querschnitt
US3992167A (en) * 1975-04-02 1976-11-16 Union Carbide Corporation Low temperature refrigeration process for helium or hydrogen mixtures using mixed refrigerant
CN115854651A (zh) * 2022-11-25 2023-03-28 浙江大学 一种利用制冷机预冷的氢液化方法及装置
CN115854651B (zh) * 2022-11-25 2023-09-15 浙江大学 一种利用制冷机预冷的氢液化方法及装置

Also Published As

Publication number Publication date
GB1135018A (en) 1968-11-27
CH451214A (de) 1968-05-15
FR1471427A (fr) 1967-03-03

Similar Documents

Publication Publication Date Title
US2909903A (en) Liquefaction of low-boiling gases
US4781033A (en) Heat exchanger for a fast cooldown cryostat
US5813250A (en) Gas liquefying method and heat exchanger used in gas liquefying method
Escanes et al. Numerical simulation of capillary-tube expansion devices
US20080142204A1 (en) Heat exchanger design for natural gas liquefaction
US3396784A (en) Honeycomed restricted tube heat exchanger
US3194025A (en) Gas liquefactions by multiple expansion refrigeration
GB1217236A (en) Method and apparatus for continuously supplying refrigeration below 4.2°k
US2492788A (en) Regenerator
WO2014150033A1 (en) Core-in-shell exchanger refrigerant inlet flow distributor
KR102552991B1 (ko) 액화 시스템
ES2254555T3 (es) Intercambiador de calor con serpentines de tubo.
US3250079A (en) Cryogenic liquefying-refrigerating method and apparatus
US3864926A (en) Apparatus for liquefying a cryogen by isentropic expansion
AU2007324597B2 (en) Method and apparatus for providing uniformity of vapour and liquid phases in a mixed stream
US1716333A (en) Heat-exchange apparatus
Chen et al. A new optimization concept of the recuperator based on Hampson-type miniature cryocoolers
US3401682A (en) Regenerative tube-bundle heat exchanger having screw-like flat-tened tubes helicallywound in spaced-apart relationship
US2433604A (en) Separation of the constituents of gaseous mixtures
Geist et al. Miniature Joule-Thomson Refrigeration Systems
US3543844A (en) Multiple-pass heat exchanger for cryogenic systems
US3257814A (en) Process for the manufacture of oxygen-enriched air
Prasad The sizing and passage arrangement of multistream plate-fin heat exchangers
Heggs Minimum temperature difference approach concept in heat exchanger networks
US3391546A (en) Refrigerating apparatus