WO1997004278A1 - Procede de refroidissement faisant appel a des gaz a bas point d'ebullition, et dispositif associe - Google Patents

Procede de refroidissement faisant appel a des gaz a bas point d'ebullition, et dispositif associe Download PDF

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Publication number
WO1997004278A1
WO1997004278A1 PCT/DE1996/001267 DE9601267W WO9704278A1 WO 1997004278 A1 WO1997004278 A1 WO 1997004278A1 DE 9601267 W DE9601267 W DE 9601267W WO 9704278 A1 WO9704278 A1 WO 9704278A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
expansion
piston
low
expander
Prior art date
Application number
PCT/DE1996/001267
Other languages
German (de)
English (en)
Inventor
Hans Quack
Christoph Haberstroh
Ole Fredrich
Original Assignee
Technische Universität Dresden
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 Technische Universität Dresden filed Critical Technische Universität Dresden
Priority to EP96926316A priority Critical patent/EP0839305A1/fr
Publication of WO1997004278A1 publication Critical patent/WO1997004278A1/fr

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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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/06—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using expanders
    • 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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size

Definitions

  • the present invention relates to a method for providing cold by means of low-boiling gases according to the preamble of claim 1, in particular for cooling superconducting devices.
  • the invention also relates to an apparatus for performing the method.
  • the low-boiling gases methane, oxygen, argon, nitrogen, neon, hydrogen or helium are used as refrigerants.
  • the refrigerant is compressed from low pressure to high pressure at ambient temperature.
  • the high pressure stream a is then cooled in a first heat exchanger 3 in countercurrent to the low pressure stream b.
  • a partial stream c is branched off and expanded to the low pressure in a work-performing expansion 4.
  • the other partial flow is further cooled after the branch point in a second and third heat exchanger 5, 6 and finally expanded into a two-phase region in a throttle valve 7 1 .
  • the liquid created after the throttling evaporates in an evaporator 8 with absorption of the cooling capacity.
  • the steam coming from the evaporator is first warmed up somewhat in the heat exchanger 6 before it is removed from the
  • REPLACEMENT BLA ⁇ (RULE 26) Expansion machine 4 coming partial stream united. Together they are warmed to ambient temperature in the second and first heat exchangers 5 and 3 (FIG. 1).
  • This type of refrigeration cycle is called the "Claude cycle”.
  • the "upper” part including the work-relieving relaxation is called the pre-cooling stage
  • the "lower” part with the third heat exchanger 6 and the throttle valve 7 1 is called the Joule-Thomson stage.
  • the division into the two partial flows is carried out at ambient temperature.
  • the pre-cooling stream c is compressed to a higher pressure 1 'and then cooled separately in the heat exchanger 3'. After its relaxation 4, it is supplied to either the high-pressure flow or the low-pressure flow (FIG. 3).
  • the object of the invention is to implement a circuit in which cold is generated in a large temperature range in many small individual expansions, but without using many expansion machines for this.
  • the object is achieved by a method having the features of claim 1.
  • Advantageous variants of the method result from subclaims 2 to 4.
  • the object is achieved by a device with the features according to claim 5.
  • a particularly advantageous embodiment results from subclaim 8.
  • the object is achieved in that the entire gas under pressure in an elongated volume is simultaneously expanded to perform work and is cooled in countercurrent by the low-pressure gas.
  • the heat transfer from the warm high-pressure gas to the cold low-pressure gas brings about a pronounced temperature gradient along the expansion volume, so that work-related expansion of the working gas can take place at any temperature level, which leads to a further reduction in the temperature.
  • a high degree of efficiency can be achieved by overlaying both process steps, when selecting suitable pressure ratios.
  • REPLACEMENT BLA ⁇ (RULE 26) Work relaxation can take place on the high pressure side, on the low pressure side or on both sides, in each case coupled with the heat transfer.
  • the object is achieved in that an expansion unit is provided in the high-pressure part, which has an elongated volume.
  • a heat exchanger ensures optimal heat transfer from high to low pressure flow.
  • the high-pressure gas does not flow evenly through the expansion volume because it is tied to the cycle of the expansion machine (inflow, expansion, pushing out). Therefore, a heat store and two volume stores have proven to be advantageous.
  • the resulting unit of heat exchanger and expansion machine forms the heat exchanger expander according to the invention (cf. FIG. 6).
  • the gas compressed in the compressor is cooled in the heat exchanger expander described above to such an extent that the state before the Joule-Thomson stage is sufficient to be able to liquefy the gas in the Joule-Thomson stage.
  • REPLACEMENT BLA ⁇ (RULE 26) Utilization of the entire high-pressure flow, ie there is no division into partial flows. As a result, a higher cooling capacity can be achieved with otherwise the same parameters, in particular the same mass flow.
  • Another advantage is the compact design of the heat exchanger expander and the resulting small chiller.
  • the compactness is due to high process pressures, relatively high pressure ratios and the inventive integration of the heat exchanger in the expansion unit.
  • the evaporator in which the liquid refrigerant, e.g. Neon, evaporated while absorbing heat, can be integrated into the heat exchanger expander or arranged separately.
  • the liquid refrigerant e.g. Neon
  • cooling capacity is available at a temperature (approx. 40 K) which is of particular interest for high-temperature superconductivity applications.
  • Fig. 5 is a schematic view of a cooling circuit with a heat exchanger expander.
  • Fig. 6 shows an embodiment of a heat exchanger expander.
  • FIG. 7 shows a section through an inventive
  • Fig. 8 is an illustration for illustrating a star-shaped piston and cylinder shape
  • Fig. 9 is an illustration for illustrating a helical piston and cylinder shape
  • FIG. 5 and 6 show a gas refrigeration cycle which e.g. can be operated with neon as the working medium.
  • the gas compressed in the compressor 1 is cooled back to ambient temperature in the downstream cooler 2.
  • the high pressure gas flows into the heat exchanger expander 14.
  • the work cycle of an oscillating relaxation machine is realized.
  • the inlet valve is closed and the gas is given the opportunity to expand while performing work.
  • the controlled outlet valve 20 opens. Now some work is required to push the gas out of the expansion chamber 22.
  • the inflow and expansion do more work than the expulsion has to do.
  • a heat flow from the high to the low pressure flow is superimposed on the work-providing relaxation.
  • the high-pressure stream is subjected to the cycle of the expansion piston 19. Therefore, a heat store 18 is required between the two flows, and two volume stores 15 and 21 on the warm and cold side.
  • REPLACEMENT BLA ⁇ (RULE 26)
  • the task of the heat accumulator takes over the wall between the heat exchanger 17 and the expansion volume 22; the line volume between compressor 1 and inlet valve 16 serves as a high-pressure accumulator and the high-pressure volume of the Joule-Thomson exchanger 6 functions as a cold medium-pressure accumulator a throttle valve 7 'or another expander 1 "can be relaxed into the 2-phase area.
  • Liquid refrigerant e.g. neon
  • the steam produced is passed in countercurrent through the heat exchanger 6 and the heat exchanger expander 14, in order then to be compressed again in the compressor.
  • Expansion piston 19 and cylinder 23 are frustoconical.
  • the heat exchanger 17 is arranged along the cylinder jacket.
  • the actual expansion volume 22 is located between the two lateral surfaces of the piston and the cylinder. At bottom dead center, the expansion volume 22 between the lateral surfaces is close to zero; Deviations are due to manufacturing tolerances. At the cold end, a small volume can remain as cold storage in the bottom dead center.
  • the expansion volume 22 can be acted upon by the high pressure gas via the valve 16 and by the seal 24 and the outlet valve
  • REPLACEMENT BLA ⁇ (RULE 26) 20 completed.
  • the expansion piston 19 performs a small stroke in relation to the extension of the expansion space 22 from the inlet valve 16 to the outlet valve 20, so that the high-pressure gas is expanded to perform a sufficient amount of work. A few millimeters of stroke are sufficient.
  • the expansion piston 19 can also be provided with a heat exchanger 17.
  • means for the flow of low pressure gas in the expansion piston 19 are provided.
  • a material or structure should be used that has anisotropic properties with regard to the thermal conductivity. All parts that are not required for the heat transfer, in the case shown the entire expansion piston, are to be made from the poorest heat-conducting material possible.
  • evacuated cavities can be provided in order to further reduce the heat flow in the piston, which flows in the direction of the main temperature gradient. An example is shown in FIG. 7. Since the expansion piston is not required as a heat exchanger, a vacuum chamber 25 is located inside the piston. The procedure for the cylinder is similar. On the one hand to reduce heat losses through longitudinal heat conduction and on the other hand to thermally isolate the heat exchanger expander from the environment.
  • the piston and cylinder jacket surface can be designed in a star shape.
  • REPLACEMENT BLA ⁇ (RULE 26) Basic shape according to FIG. 7 is retained. Like the expansion piston 19 in FIG. 7, the “star piston” is guided by a linear actuator.
  • FIG. 9 shows a variant with a spiral or helical profiled expansion piston 19. Only the expansion piston is shown in the figure.
  • the cylinder has a correspondingly designed outer surface.
  • the expansion piston carries out a rotating up and down movement, similar to the movement of a threaded spindle, for the work-relieving expansion of the high pressure gas and its discharge.
  • expansion pistons and cylinders have a small closed clearance space at the bottom dead center.
  • the surfaces of the expansion piston and cylinder must be similar to one another, except for manufacturing-related tolerances, and the lower dead center of the piston must be controlled precisely. Exact guidance of the expansion piston during the working cycle is also important for the perfect sealing of the expansion volume.
  • REPLACEMENT BLA ⁇ (RULE 26) a - high pressure flow b - low pressure flow c - precooling flow

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)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

L'invention concerne un procédé et un dispositif permettant l'obtention de basses températures au moyen de gaz à bas point d'ébullition. Selon l'invention, un gaz en circulation est soumis à une pression élevée par un compresseur (1), le refroidissement est obtenu au moyen de machines à détente (14), et le gaz sous haute pression se refroidit en libérant sa chaleur dans l'échangeur de chaleur à contre courant (17), tandis que le gaz sous basse pression est chauffé par absorption de chaleur dans ledit échangeur de chaleur à contre-courant. Au moins un courant partiel, dans une partie de circuit, subit, simultanément dans le même dispositif (14), une détente fournissant un travail et un échange de chaleur avec récupération.
PCT/DE1996/001267 1995-07-14 1996-07-12 Procede de refroidissement faisant appel a des gaz a bas point d'ebullition, et dispositif associe WO1997004278A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP96926316A EP0839305A1 (fr) 1995-07-14 1996-07-12 Procede de refroidissement faisant appel a des gaz a bas point d'ebullition, et dispositif associe

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE19525638.7 1995-07-14
DE1995125638 DE19525638C2 (de) 1995-07-14 1995-07-14 Kühlverfahren mittels tiefsiedender Gase und Vorrichtung zur Durchführung des Verfahrens
DE1996128205 DE19628205C2 (de) 1995-07-14 1996-07-12 Vorrichtung zur Durchführung eines Kühlverfahrens mittels tiefsiedender Gase nach dem Patent 195 25 638
DE19628205.5 1996-07-12

Publications (1)

Publication Number Publication Date
WO1997004278A1 true WO1997004278A1 (fr) 1997-02-06

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PCT/DE1996/001267 WO1997004278A1 (fr) 1995-07-14 1996-07-12 Procede de refroidissement faisant appel a des gaz a bas point d'ebullition, et dispositif associe

Country Status (3)

Country Link
EP (1) EP0839305A1 (fr)
DE (2) DE19525638C2 (fr)
WO (1) WO1997004278A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19525638C2 (de) * 1995-07-14 1998-04-09 Univ Dresden Tech Kühlverfahren mittels tiefsiedender Gase und Vorrichtung zur Durchführung des Verfahrens
DE19812495C2 (de) * 1998-03-21 2000-09-28 Lutz Mardorf Verfahren zum Betrieb einer Wärmepumpenanlage oder Kältemaschinenanlage und zur Durchführung dieses Verfahrens geeignete Komponenten

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1499489A (en) * 1919-07-03 1924-07-01 Raymond W Tibbetts Refrigerating apparatus
US1619197A (en) * 1924-04-25 1927-03-01 Chicago Pneumatic Tool Co Heat engine
DE609405C (de) * 1933-01-04 1935-02-14 Aeg Luftkaeltemaschine
US2993341A (en) * 1958-02-03 1961-07-25 Alwin B Newton Hot gas refrigeration system
DE1288615B (de) * 1963-03-27 1969-02-06 Dubinsky Moisei G Vorrichtung zur Kuehlung einer Kammer
US3986361A (en) * 1975-07-30 1976-10-19 Michael Eskeli Turbine with regeneration
US4189930A (en) * 1977-06-17 1980-02-26 Antipenkov Boris A Method of obtaining refrigeration at cryogenic level
GB2083601A (en) * 1980-09-08 1982-03-24 Vnii Gelieevoj Tech A method and plant for refrigeration
SU1408165A1 (ru) * 1985-04-17 1988-07-07 Краснодарский политехнический институт Способ работы газовой холодильной машины
US4873831A (en) * 1989-03-27 1989-10-17 Hughes Aircraft Company Cryogenic refrigerator employing counterflow passageways

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL6402127A (fr) * 1964-03-04 1965-09-06
DE19525638C2 (de) * 1995-07-14 1998-04-09 Univ Dresden Tech Kühlverfahren mittels tiefsiedender Gase und Vorrichtung zur Durchführung des Verfahrens

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1499489A (en) * 1919-07-03 1924-07-01 Raymond W Tibbetts Refrigerating apparatus
US1619197A (en) * 1924-04-25 1927-03-01 Chicago Pneumatic Tool Co Heat engine
DE609405C (de) * 1933-01-04 1935-02-14 Aeg Luftkaeltemaschine
US2993341A (en) * 1958-02-03 1961-07-25 Alwin B Newton Hot gas refrigeration system
DE1288615B (de) * 1963-03-27 1969-02-06 Dubinsky Moisei G Vorrichtung zur Kuehlung einer Kammer
US3986361A (en) * 1975-07-30 1976-10-19 Michael Eskeli Turbine with regeneration
US4189930A (en) * 1977-06-17 1980-02-26 Antipenkov Boris A Method of obtaining refrigeration at cryogenic level
GB2083601A (en) * 1980-09-08 1982-03-24 Vnii Gelieevoj Tech A method and plant for refrigeration
SU1408165A1 (ru) * 1985-04-17 1988-07-07 Краснодарский политехнический институт Способ работы газовой холодильной машины
US4873831A (en) * 1989-03-27 1989-10-17 Hughes Aircraft Company Cryogenic refrigerator employing counterflow passageways

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
DATABASE WPI Section Ch Week 8904, Derwent World Patents Index; Class J07, AN 89-030685, XP002019699 *

Also Published As

Publication number Publication date
DE19628205A1 (de) 1998-01-15
DE19525638C2 (de) 1998-04-09
DE19628205C2 (de) 1998-06-10
DE19525638A1 (de) 1997-01-16
EP0839305A1 (fr) 1998-05-06

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