EP3191712B1 - Dispositif de compression, dispositif de refroidissement équipé de celui-ci et procédé pour faire fonctionner le dispositif de compression et le dispositif de refroidissement - Google Patents

Dispositif de compression, dispositif de refroidissement équipé de celui-ci et procédé pour faire fonctionner le dispositif de compression et le dispositif de refroidissement Download PDF

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Publication number
EP3191712B1
EP3191712B1 EP15774869.0A EP15774869A EP3191712B1 EP 3191712 B1 EP3191712 B1 EP 3191712B1 EP 15774869 A EP15774869 A EP 15774869A EP 3191712 B1 EP3191712 B1 EP 3191712B1
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Prior art keywords
gas
pressure
compressor
working
working gas
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EP15774869.0A
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German (de)
English (en)
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EP3191712A1 (fr
Inventor
Jens HÖHNE
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Pressure Wave Systems GmbH
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Pressure Wave Systems GmbH
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Priority to EP18195959.4A priority Critical patent/EP3434897B1/fr
Publication of EP3191712A1 publication Critical patent/EP3191712A1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B37/00—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00
    • F04B37/10—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00 for special use
    • F04B37/12—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00 for special use to obtain high pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B45/00—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids
    • F04B45/02—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids having bellows
    • F04B45/022—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids having bellows with two or more bellows in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B37/00—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00
    • F04B37/10—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00 for special use
    • F04B37/18—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00 for special use for specific elastic fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B45/00—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids
    • F04B45/02—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids having bellows
    • F04B45/024—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids having bellows with two or more bellows in series
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B45/00—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids
    • F04B45/02—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids having bellows
    • F04B45/033—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids having bellows having fluid drive
    • 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
    • F25B9/02—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using Joule-Thompson effect; using vortex effect

Definitions

  • the invention relates to a compressor device, a cooling device equipped therewith and a method for operating the compressor device.
  • pulse tube coolers or Gifford-McMahon coolers are used for cooling magnetic resonance tomographs, cryopumps, etc.
  • Gas and especially helium compressors are used in combination with rotary or rotary valves.
  • the rate at which compressed helium is introduced and re-circulated to the cooling device is in the range of 1 Hz.
  • a problem with conventional screw or piston compressors is that oil from the compressor may enter and contaminate the working gas and thus the cooling device ,
  • acoustic compressors or high-frequency compressors in which one or more pistons are caused by a magnetic field in linear resonant vibrations. These resonant frequencies are in the range of a few 10 Hz and are therefore not suitable for use with pulse tube coolers and Gifford-McMahon coolers to produce very low temperatures in the lower than 10 K range.
  • a membrane compressor or pump which has a working space that is divided into a gas volume and a liquid volume by an elastic, gas and liquid-tight membrane.
  • a liquid pump liquid is periodically pressed into the liquid volume of the working space, whereby the elastic membrane expands in the direction of gas volume and this compresses - compressor function - or pushing out of the gas volume - pump function.
  • a disadvantage is the fact that the gas-, liquid-tight and pressure-resistant sealing of the elastic membrane in the working space is relatively expensive. Especially in the field of sealing, the membrane is heavily loaded, so that either very expensive materials must be used or a shorter life has to be accepted.
  • CH 457 147 A also shows a membrane compressor and mentions the lack of tightness of the membrane to helium.
  • DE 20 2007 018538 U1 shows a multi-stage diaphragm suction pump whose pumping chambers work in parallel or serially.
  • a heat pump and a refrigerator with a compressor device are known.
  • the compressor device comprises a compressor chamber in which a balloon is arranged.
  • the balloon is periodically pressurized with liquid so that the gas surrounding the balloon is periodically compressed and relaxed again.
  • the disadvantage here is that the balloon envelope can scrape or rub in certain operating conditions on the hard and possibly edged inner surface of the compressor chamber. As a result, due to the pressure conditions hole or cracking in the balloon envelope occur.
  • the permeability - permeability - of the balloon envelope for helium as a working gas is too large, so you quickly lose substantial amounts of helium. Thus, the service life of such systems with balloon is unsatisfactory.
  • a diaphragm pump for liquids which can also serve as a "gas compression pump".
  • a liquid must be introduced between the membrane and pump valves, ie a liquid is provided in the gas space. It is thus a compression device with a liquid stamp. A physical separation between compressed gas and hydraulic fluid therefore does not take place.
  • DE 10 2008 060598 A1 shows an apparatus for compressing a gas, comprising two cylinder filled with a hydraulic fluid or a working gas. The hydraulic fluid is preferably pumped back and forth between these cylinders with a hydraulic pump. Again, the physical separation between gas and liquid is not sufficient.
  • US 1 580 479 A describes a diaphragm pump with two chambers (or bellows) without working fluid, which are mutually compressed or relaxed via a yoke separating the chambers.
  • WO2014 / 016415A2 is a compressor device with a metal bellows known as a compressor element, which is impermeable to hydrogen except for all possible working gases.
  • the working gas may be due to the Metal bellows are also kept oil-free.
  • the efficiency due to the interaction with the working fluid balance tank is unsatisfactory.
  • the common pumping device is used twice. In each flow direction of the working fluid is a compression of the working gas; in the one flow direction in the first compressor stage and in the opposite direction of flow in the second compressor stage. This increases the efficiency of the compressor device. Characterized in that the high and low pressure gas line are designed so that they act as a gas storage due to their volume, the operating frequency of a compressor operated with the device cooler can be decoupled from the pumping frequency of the pumping device.
  • the compressed working gas is cooled after each compression stroke.
  • first working gas in the first compressor stage is compressed or precompressed and stored temporarily in a buffer memory.
  • the second compressor stage is operated virtually idle and serves as a working fluid expansion tank. If in the buffer memory, a working gas at a mean pressure p mid is reached, which corresponds to the second gas volume in the second compressor stage, in the next compressor stroke in the second compressor stage, the pre-compressed working gas from the buffer memory to the final pressure p end is compressed. The compressed to the final pressure p end working gas is then discharged to the outside or stored in a high-pressure gas storage.
  • first working gas in the first compressor stage is compressed or precompressed and simultaneously transferred to the second gas volume of the second compressor stage.
  • the pre-compressed working gas to the mean pressure p mid is then compressed to the final pressure p end .
  • the compressed to the final pressure p end working gas is then discharged to the outside or stored in a high-pressure gas storage.
  • a working fluid preferably hydraulic oil according to DIN 51524 is used, which is additionally dehydrated or anhydrous.
  • the hydraulic oil is in a closed system of pumping device, working fluid equalizing device and fluid volume in the compressor chamber, so that during operation no water from the environment can be absorbed by the hydraulic oil.
  • water can also be used as the working fluid.
  • Water as a working fluid is also advantageous because in the event of defects, water that has penetrated into a downstream cryocooler can be removed more easily than hydraulic oil that has entered a downstream cooler.
  • water is suitable as a working medium in explosion-protected applications, since water is non-flammable and non-explosive. In addition, water is non-toxic and therefore environmentally friendly.
  • helium, neon or nitrogen is preferably used as working gas.
  • Fig. 1 shows an unclaimed compressor device with a first and a second compressor stage 2-1, 2-2, in the form of a non-promoting compressor device.
  • Each of the two compressor devices 2-1, 2-2 has a gas-tight closed compressor chamber 4-1, 4-2.
  • a metal bellows 6-1, 6-2 is arranged in each of the two compressor rooms 4-1, 4-2.
  • the metal bellows 6-1, 6-2 subdivide the compressor chambers 4-1, 4-2 into a first and a second gas volume 8-1, 8-2 for a working gas 10 and into a first and second fluid volume 12-1, 12, respectively -2 for a working liquid 14.
  • the gas volumes 8-1, 8-2 are inside the metal bellows 6-1, 6-2, and the liquid volumes are outside the bellows 6-1, 6-2.
  • the gas volumes 8-1, 8-2 are each provided with a high pressure working gas port 18-1, 18-2 and a low pressure working gas port 20-1, 20-2 connected.
  • the low pressure working gas ports 20-1, 20-2 are provided with check valves 22 which are permeable toward the compressor stages 2-1, 2-2.
  • the high pressure working gas ports 18-1, 18-2 are also provided with check valves 22 having opposite directions of passage as compared to the check valves 22 on the low pressure working gate ports 20-1, 20-2.
  • the high pressure working gas ports 18-1, 18-2 are connected via the check valves 22 to a common high pressure gas line 24, and the low pressure working gas ports 20-1, 20-2 are connected to a low pressure gas line 26 via the check valves 22.
  • the check valves 22 in the high-pressure working gas ports 18-1, 18-2 are in the direction of common high-pressure gas line 24 and the check valves 22 on the low-pressure working gas ports 20-1, 20-2 are in the direction of compressor stages 2-1, 2-2 permeable.
  • the common high pressure gas line 24 and the common low pressure gas line 26 terminate in a motorized rotary valve 28 which alternately the high pressure gas line 24 and the low pressure gas line 26 with a cooling device 30, for.
  • the high and low pressure gas line 24, 26 act due to their volume as a gas storage or it is explicitly a low-pressure gas storage 27 and a high-pressure gas storage 25 in the low-pressure or high-pressure gas line 26, 24 are provided.
  • the check valves 22 at the two high pressure working gas ports 18-1, 18-2 are each followed by heat exchangers 32-1, 32-2 for cooling the compressed working gas.
  • the two compressor stages 2-1, 2-1 are constructed analogously, ie, the gas volumes 8-1, 8-2 and the liquid volumes 12-1, 12-2 are equal.
  • the two working fluid ports 16-1, 16-2 are connected to a common electromotive pumping device 34, which alternately pumps working fluid 14 into the first and second fluid volumes 12-1, 12-2 of the first and second compressor stages 2-1, 2-2. Ie. either working fluid 14 is pumped from the second fluid volume 12-2 into the first fluid volume 12-1 or vice versa.
  • FIGS. 2a to 2e illustrate the various phases of operation of the compressor device Fig. 1 , In the in Fig. 2a phase shown by the common Pumping 34 working fluid 14 from the second fluid volume 12-2 of the second compressor stage 2-2 in the first fluid volume 12-1 in the first compressor stage 2-1 pumped.
  • the first metal bellows 6-1 is compressed and the working gas 10 therein is pressed into the high pressure gas reservoir 25 via the first high pressure working gas port 18-1, the first heat exchanger 32-1 and the common high pressure gas line 24.
  • the second metal bellows 6-2 expands through working gas 10, which flows back out of the low-pressure working gas reservoir 27 via the low-pressure gas line 26 and the second low-pressure working gas connection 20-2.
  • the rotary valve 28 connects the cooling device 30 via the low pressure gas line 26 with the low pressure gas storage 27th
  • the working fluid flow is reversed and the pumping device 34 now pumps working fluid 14 from the first fluid volume 12-1 of the first compressor stage 2-1 in the second fluid volume 12-2 in the second compressor stage 2-2.
  • the second metal bellows 6-2 is compressed and the working gas 10 therein is compressed and pressed into the high pressure gas reservoir 25 via the second high pressure working gas port 18-1, the second heat exchanger 32-2 and the common high pressure gas line 24.
  • the first metal bellows 6-1 expands through working gas 10 flowing back from the low-pressure gas reservoir 27 via the low-pressure gas line 26 and the first low-pressure working gas port 20-1.
  • Fig. 2e phase shown is again the first phase and the compression takes place in the first compressor stage 2-1.
  • Fig. 2a and 2e differ only in that in Fig. 2e the first metal bellows 6-1 still relaxed and the second metal bellows 6-2 is still compressed.
  • Fig. 2a is the compression in the first compressor stage 2-1 completed and the first metal bellows 6-1 is compressed, while the second metal bellows 6-2 is relaxed.
  • the rotational frequency of the rotary valve 28 is decoupled from the frequency of the compression in the two compressor stages.
  • the rotational frequency of the rotary valve 28 may be synchronized with the frequency of the compressor strokes.
  • the high-pressure and low-pressure gas storage 25, 27 could be dispensed with.
  • Fig. 3 shows the invention with two compressor stages 2-1, 2-2 in the form of a working gas 10 promotional compressor device.
  • the structure of the two compressor stages 2-1, 2-2 and the connection of the two compressor stages 2-1, 2-2 with the common pumping device (34) corresponds to the structure in Fig. 1 and 2
  • that of the two heat exchangers 32-1, 32-2 corresponds to the arrangement according to the first embodiment.
  • the working gas 10 is first compressed in the first compressor stage 2-1 from an initial pressure po to a first average pressure p mid1 and then subsequently in the second compressor stage 2-2 from a second average pressure p mid2 to the final pressure p end .
  • a buffer store 42 is connected via a first gas line 40-1 and a first shut-off valve 44-1 to the second low-pressure working gas port 20-2 of the second compressor stage 2-2.
  • the first high pressure Pakistangansan gleich 20-1 is connected to the buffer memory 42.
  • a low-pressure gas storage 27 is connected via a third gas line 40-3 to a first low-pressure working gas connection 20-1 with a check valve 22 in the first compressor stage 2-1.
  • the second high pressure working gas connection 18-2 of the second compressor stage 2-2 is connected via a check valve 22, a second heat exchanger 32- 2 and a fourth gas line 40-4 with a high-pressure gas storage 25.
  • the first compressor stage 2-1 is supplied with working gas 10 to be compressed from the low-pressure gas reservoir 27.
  • FIGS. 4a to 4d the operation of the compressor device after Fig. 3 described.
  • first phase is pumped by the common pumping device 34 working fluid 14 from the first fluid volume 12-1 of the first compressor stage 2-1 in the second fluid volume 12-2 in the second compressor stage 2-1.
  • the first metal bellows 6-1 expands and uncompressed working gas 10 flows via the third gas line 40-3 and the first low-pressure working gas connection 20-1 with check valve 22 into the first gas volume 8-1.
  • the first check valve 44-1 in the first gas line is closed.
  • the second compressor stage 2-2 serves only as a working fluid expansion tank. In the second gas volume 8-2 prevails in the relaxed state, the second average pressure p mid2 and in the compressed state in about the final pressure p end .
  • the first shut-off valve 40-1 is opened during the next compression stroke in the first compressor stage 2-1, so that the working gas 10 pre-compressed to the first average pressure p mid1 from the buffer reservoir 42 via the open first shut-off valve 44th -1 and the first gas line 40-1 can flow into the second gas volume 8-2 of the second compressor stage 2-2, wherein the second average pressure p mid2 sets - see Fig. 4c ,
  • the working fluid 14 is pumped through the common pumping device 34 in the second compressor stage 2-2.
  • the working gas 10 pre-compressed to the second average pressure p mid2 in the second gas volume 8-2 is at the final pressure p end . further compressed and pressed via the second heat exchanger 32-2 and the fourth gas line 40-4 in the high-pressure gas storage 25.
  • the first high-pressure working gas connection 18-1 is connected via a gas line 40-1, 40-2 to the low-pressure working gas connection 20-2 of the second compressor stage 2-2.
  • the buffer memory 42 and the first shut-off valve 44-1 are unnecessary.
  • the working gas 10 is pre-compressed in the first compressor stage 2-1 to a mean pressure p mid and in the countermovement of the common electromotive Pumpeninheimtung 34, the working gas 10 in the second compressor stage 2-2 then compressed to the final pressure p end .
  • the compressed to the final pressure p end working gas is then discharged to the outside or stored in a high-pressure gas storage 25.
  • Fig. 5 shows an application as a drive of a Joule-Thomson refrigerator 50 with closed working gas circuit.
  • Hydraulic oils according to DIN 51524 are suitable as working fluids. These H, HL, HLP and HVLP oils are oils which are well tolerated with common sealants such as NBR (acrylonitrile-butadiene rubber) etc. NBR, however, is not sufficiently helium-tight. HF oils are often incompatible with common sealing materials ( http://de.wikipedia.org/wiki/List of plastics ).
  • water can also be used as the working fluid.
  • Water as a working fluid is also advantageous because in the event of defects, water that has penetrated into a downstream cryocooler can be removed more easily than hydraulic oil that has entered a downstream cooler.
  • water is suitable as a working medium in explosion-protected applications, since water is non-flammable and non-explosive. In addition, water is non-toxic and therefore environmentally friendly.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Reciprocating Pumps (AREA)

Claims (9)

  1. Dispositif compresseur avec
    un premier étage compresseur (2-1), qui comporte
    un premier espace de compression (4-1) avec un volume défini, dans lequel un premier soufflet métallique (6-1) subdivise le premier espace de compression (4-1) en un premier volume de gaz (8-1) avec un gaz de travail (10) et un premier volume de fluide (12-1) avec un fluide de travail (14),
    un premier raccord de gaz de travail à haute pression (18-1) et un premier raccord de gaz de travail à basse pression (20-1) qui débouchent dans le premier volume de gaz (8-1) et
    un premier raccord de fluide de travail (16-1) qui débouche dans le premier volume de fluide (12-1) ; et
    un dispositif de pompage (34), qui pompe périodiquement le fluide de travail (14) jusque dans le volume de fluide (12-1) via le premier raccord de fluide de travail (16-1) et qui comprime ainsi périodiquement le gaz de travail (10) dans le volume de gaz (8-1),
    caractérisé en ce que
    il est prévu un deuxième étage compresseur (2-2), qui comprend un deuxième espace de compression (4-2) qu'un deuxième soufflet métallique (8-2) subdivise en un deuxième volume de gaz (8-2) avec du gaz de travail (10) et un deuxième volume de fluide (12-2) avec du fluide de travail (14),
    le deuxième étage compresseur (2-2) comprend un deuxième raccord de gaz de travail à haute pression (18-2) et un deuxième raccord de gaz de travail à basse pression (20-2) qui débouchent dans le deuxième volume de gaz (8-2),
    le deuxième étage compresseur (2-2) comprend un deuxième raccord de fluide de travail (16-2) qui débouche dans le deuxième volume de fluide (12-2),
    le dispositif de pompage (34) est un dispositif de pompage commun,
    le dispositif de pompage commun (34) est relié au deuxième étage compresseur (2-2) via le deuxième raccord de fluide de travail (16-2),
    le deuxième raccord de gaz de travail à basse pression (20-2) du deuxième étage compresseur (2-2) est relié à un réservoir tampon (42) via une première conduite de gaz (40-1) et un premier clapet anti-retour (44-1), et
    le premier raccord de gaz de travail à haute pression (18-1) du premier étage compresseur (2-1) est relié au réservoir tampon (42) via une deuxième conduite de gaz (40-2).
  2. Dispositif compresseur avec
    un premier étage compresseur (2-1), qui comporte
    un premier espace de compression (4-1) avec un volume défini, dans lequel un premier soufflet métallique (6-1) subdivise le premier espace de compression (4-1) en un premier volume de gaz (8-1) avec un gaz de travail (10) et un premier volume de fluide (12-1) avec un fluide de travail (14),
    un premier raccord de gaz de travail à haute pression et un premier raccord de gaz de travail à basse pression (18-1, 20-1) qui débouchent dans le premier volume de gaz (8-1) et
    un premier raccord de fluide de travail (16-1) qui débouche dans le premier volume de fluide (12-1) ; et
    un dispositif de pompage (34), qui pompe périodiquement le fluide de travail (14) jusque dans le volume de fluide (12-1) via le premier raccord de fluide de travail (16-1) et qui comprime ainsi périodiquement le gaz de travail (10) dans le volume de gaz (8-1),
    caractérisé en ce que
    il est prévu un deuxième étage compresseur (2-2), qui comprend un deuxième espace de compression (4-2) qu'un deuxième soufflet métallique (8-2) subdivise en un deuxième volume de gaz (8-2) avec du gaz de travail (10) et un deuxième volume de fluide (12-2) avec du fluide de travail (14),
    le deuxième étage compresseur (2-2) comprend un deuxième raccord de gaz de travail à haute pression et un deuxième raccord de gaz de travail à basse pression (18-2, 20-2) qui débouchent dans le deuxième volume de gaz (8-2),
    le deuxième étage compresseur (2-2) comprend un deuxième raccord de fluide de travail (16-2) qui débouche dans le deuxième volume de fluide (12-2),
    le dispositif de pompage (34) est un dispositif de pompage commun,
    le dispositif de pompage commun (34) est relié au deuxième étage compresseur (2-2) via le deuxième raccord de fluide de travail (16-2),
    le deuxième raccord de gaz de travail à basse pression (20-2) du deuxième étage compresseur (2-2) est relié au premier raccord de gaz de travail à haute pression (18-1) du premier étage compresseur (2-1) via une conduite de gaz (40-1 ; 40-2).
  3. Dispositif compresseur selon la revendication 1 ou 2, caractérisé en ce que
    les raccords de gaz de travail à haute pression (18-1, 18-2) et les raccords de gaz de travail à basse pression (20-1, 20-2) des deux étages compresseurs (2-1, 2-2) sont munis à chaque fois de clapets anti-retour (22),
    les clapets anti-retour (22) au niveau des raccords de gaz de travail à basse pression (20-1, 20-2) sont passants à chaque fois en direction des étages compresseurs (2-1, 2-2), et
    les clapets anti-retour (22) au niveau des raccords de gaz de travail à haute pression (18-1, 18-2) sont passants dans la direction opposée en comparaison des clapets anti-retour au niveau des raccords de gaz de travail à basse pression (20-1, 20-2).
  4. Dispositif compresseur selon l'une quelconque des revendications précédentes 1 à 3, caractérisé en ce qu'un échangeur de chaleur (32-1, 32-2) est placé à chaque fois en aval des raccords de gaz de travail à haute pression (18-1, 18-2) des deux étages compresseurs (2-1, 2-2) afin de refroidir le gaz de travail (10) comprimé.
  5. Dispositif compresseur selon l'une quelconque des revendications précédentes 1 à 4, caractérisé en ce que
    la première conduite de gaz de travail à basse pression (20-1) est reliée à un réservoir de gaz à basse pression (27) via une troisième conduite de gaz (40-3), et
    la deuxième conduite de gaz de travail à haute pression (18-1) du deuxième étage compresseur (2-2) est reliée à un réservoir de gaz à haute pression (25) via une quatrième conduite de gaz (40-4).
  6. Dispositif de refroidissement avec un dispositif compresseur selon la revendication 5 et avec un refroidisseur de Joule-Thomson (50) qui est relié au réservoir de gaz à basse pression (27) et au réservoir de gaz à haute pression (25).
  7. Procédé de fonctionnement d'un dispositif compresseur selon l'une quelconque des revendications 1, 3, 4 ou 5 et d'un dispositif de refroidissement selon la revendication 6, avec les étapes de procédé :
    - compression multiple de gaz de travail (10) dans le premier étage compresseur (2-1) d'une pression initiale (p0) à une première pression moyenne (pmid1), le deuxième étage compresseur (2-2) servant de récipient de compensation de fluide de travail ;
    - stockage temporaire du gaz de travail (10), précomprimé à la première pression moyenne (pmid1), dans un réservoir tampon (42) ;
    - répétition des étapes de procédé précédentes jusqu'à ce que, lors de la liaison du réservoir tampon (42) avec le deuxième volume de gaz (8-2) dans le deuxième étage compresseur (2-2), il s'installe dans le deuxième volume de gaz (8-2) une deuxième pression moyenne (pmid2), avec pmid1 > pmid2 ;
    - transfert du gaz de travail (10), précomprimé à la première pression moyenne (pmid1), du réservoir tampon (42) au volume de gaz (8-2) du deuxième étage compresseur (2-1) ; et
    - compression du gaz de travail (10) précomprimé à la deuxième pression moyenne (pmid2) dans le deuxième étage compresseur (2-2) à la pression finale (pend).
  8. Procédé de fonctionnement d'un dispositif compresseur selon l'une quelconque des revendications 2 à 5 et d'un dispositif de refroidissement selon la revendication 6, avec les étapes de procédé :
    - compression de gaz de travail (10) dans le premier étage compresseur (2-1) d'une pression initiale (p0) à une pression moyenne (pmid) et transfert du gaz de travail (10) précomprimé à la pression moyenne (pmid) jusque dans le deuxième volume de gaz (8-2) du deuxième étage compresseur (2-2) ; et
    - compression du gaz de travail (10) précomprimé à la pression moyenne (pmid) dans le deuxième étage compresseur (2-2) à la pression finale (pend).
  9. Procédé selon la revendication 7 ou 8, caractérisé en ce que le gaz de travail comprimé (10) issu des deux étages compresseurs (2-1, 2-2) est refroidi après chaque course de compresseur.
EP15774869.0A 2014-09-08 2015-09-08 Dispositif de compression, dispositif de refroidissement équipé de celui-ci et procédé pour faire fonctionner le dispositif de compression et le dispositif de refroidissement Active EP3191712B1 (fr)

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DE102014217897.5A DE102014217897A1 (de) 2014-09-08 2014-09-08 Kompressorvorrichtung, eine damit ausgerüstete Kühlvorrichtung und ein Verfahren zum Betreiben der Kompressorvorrichtung und der Kühlvorrichtung
PCT/EP2015/070507 WO2016038041A1 (fr) 2014-09-08 2015-09-08 Dispositif de compression, dispositif de refroidissement équipé de celui-ci et procédé pour faire fonctionner le dispositif de compression et le dispositif de refroidissement

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EP18195959.4A Division-Into EP3434897B1 (fr) 2014-09-08 2015-09-08 Dispositif compresseur, dispositif de refroidissement équipé d'un tel dispositif compresseur et procédé de fonctionnement du dispositif compresseur et du dispositif de refroidissement

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EP18195959.4A Active EP3434897B1 (fr) 2014-09-08 2015-09-08 Dispositif compresseur, dispositif de refroidissement équipé d'un tel dispositif compresseur et procédé de fonctionnement du dispositif compresseur et du dispositif de refroidissement

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US (1) US11028841B2 (fr)
EP (2) EP3191712B1 (fr)
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WO (1) WO2016038041A1 (fr)

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Also Published As

Publication number Publication date
EP3434897B1 (fr) 2019-12-11
US20170175729A1 (en) 2017-06-22
JP6594959B2 (ja) 2019-10-23
EP3191712A1 (fr) 2017-07-19
DE102014217897A1 (de) 2016-03-10
WO2016038041A1 (fr) 2016-03-17
EP3434897A1 (fr) 2019-01-30
CN107094367B (zh) 2019-10-25
JP2017528644A (ja) 2017-09-28
CN107094367A (zh) 2017-08-25
US11028841B2 (en) 2021-06-08

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