WO2023247277A1 - Dispositif de compresseur, et dispositif de refroidissement doté d'un dispositif de compresseur - Google Patents

Dispositif de compresseur, et dispositif de refroidissement doté d'un dispositif de compresseur Download PDF

Info

Publication number
WO2023247277A1
WO2023247277A1 PCT/EP2023/065892 EP2023065892W WO2023247277A1 WO 2023247277 A1 WO2023247277 A1 WO 2023247277A1 EP 2023065892 W EP2023065892 W EP 2023065892W WO 2023247277 A1 WO2023247277 A1 WO 2023247277A1
Authority
WO
WIPO (PCT)
Prior art keywords
compressor
piston
space
cylinder
working
Prior art date
Application number
PCT/EP2023/065892
Other languages
German (de)
English (en)
Inventor
Jens HÖHNE
Original Assignee
Pressure Wave Systems Gmbh
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 Pressure Wave Systems Gmbh filed Critical Pressure Wave Systems Gmbh
Publication of WO2023247277A1 publication Critical patent/WO2023247277A1/fr

Links

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
    • 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
    • F04B45/0333—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids having bellows having fluid drive the fluid being actuated directly by a piston
    • 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
    • F25B31/00—Compressor arrangements

Definitions

  • Compressor device and cooling device with compressor device are Compressor device and cooling device with compressor device
  • the present disclosure relates to a compressor device and a cooling device with the compressor device and a Gifford-McMahon cooler or a pulse tube cooler.
  • Pulse tube coolers or Gifford-McMahon coolers are widely used to cool magnetic resonance tomographs, cryo pumps, quantum computers, quantum communication systems and the like.
  • Gas and especially helium compressors are used in combination with rotary or rotary valves.
  • a helium compressor is connected to a rotary valve via a high-pressure line and a low-pressure line.
  • the rotary valve On the output side, the rotary valve is connected via a gas line to a cooling device in the form of a Gifford-McMahon cooler or a pulse tube cooler.
  • the high and low pressure side of the gas compressor is alternately connected to the pulse tube cooler or the Gifford-Mcmahon cooler via the rotary valve.
  • the rate at which the compressed helium is introduced into the cooling device and discharged again is in the range of 1-2 Hz.
  • the disadvantage of such cooling or compressor systems is that the motor-driven rotary valve causes losses of approximately 50% of the compressor's input power caused.
  • Cooling devices with pulse tube coolers or Gifford-McMahon coolers are known from DE 101 37 552 C1.
  • DE 633 104 A discloses a compressor device with a compressor device in which a working medium is periodically compressed and expanded again by a reciprocating compressor element in the form of a piston.
  • the drive device includes a printing cylinder with a back and forth moving piston.
  • the drive device is mechanically coupled to the compressor element.
  • Both the drive device and the compressor element are constructed with individual pressure cylinders in which a compressor or compressor piston is mounted.
  • the drive device and compressor element are mechanically connected, with the feedthroughs from the pressure cylinders being sealed.
  • This structure requires a relatively large amount of space for the apparatus because the printing cylinders are arranged in series.
  • the design requires the use of two pistons and two bushings, which are structurally complex and prone to failure in terms of leaks.
  • the object of the present invention is to eliminate or at least reduce the disadvantages of the prior art. Specifically, it is the object of the present invention to provide a compressor device and a cooling system which minimizes losses and installation space.
  • the object is achieved by a compressor device with a cylinder, a piston arranged within the cylinder, which delimits a transfer space filled with a transfer fluid and can be periodically moved back and forth by means of a drive device, a compressor element arranged within the transfer space, preferably bellows, in particular metal bellows , which delimits a working space (compression space) filled with a working gas, and a connection via which the working space can be connected to a working gas line (pressure line) to a Gifford-McMahon cooler or a pulse tube cooler, in particular a two-stage 4K (four Kelvin) cooler is, wherein the compressor element and the working gas contained therein are periodically compressed/compressed indirectly via the transfer fluid displaced by the piston.
  • the compressor device includes the cylinder with a cylinder bore formed on an inside of the cylinder and in the cylinder running piston with a piston skirt formed in the circumferential direction of the piston.
  • the piston skirt slides sealingly on the cylinder bore of the cylinder.
  • at least one annular seal/piston ring is formed between the piston skirt and the cylinder bore.
  • the piston further includes a piston roof, which faces and delimits the transfer space filled with the transfer fluid.
  • the piston is provided and designed to carry out a periodic linear movement in a direction of a cylinder center fiber (cylinder center axis), which extends in a cylinder longitudinal direction.
  • the compressor element is formed in the transmission space and contains at least one, preferably accordion-shaped, wall.
  • the compressor element is preferably designed as a bellows.
  • the compressor element surrounds the working space filled with the working gas.
  • the compressor element separates the working space from the transmission space.
  • the working space is designed with the connection, which connects the working space to the working gas line in a fixed or detachable manner.
  • the connection is preferably formed on a side of the compressor element facing away from the piston.
  • the working gas line is provided and designed to connect the working space to the Gifford-Mcmahon cooler or the pulse tube cooler or any other suitable cooler.
  • the volume of the work space is variable due to the preferably accordion-shaped wall. Due to the linear movement of the piston, a force is exerted/transmitted to the compressor element by means of the transmission fluid and the working gas contained in the working space is periodically compressed/compressed and expanded.
  • the core of the invention is therefore to periodically compress and expand the working gas contained in the compressor element of the compressor device by moving the piston indirectly by means of the transfer fluid.
  • the core of the invention is that a pressure generation location (force generation location) and a compression location are formed in a cylinder.
  • piston and the compressor element are mechanically decoupled.
  • the piston and the compressor element are arranged in the cylinder in such a way that they never touch each other.
  • the force acting on the piston or the force to be transmitted by the piston is transmitted exclusively hydraulically to the compressor element.
  • a mechanical connection between the piston and the compressor element for power transmission is dispensed with in the present invention.
  • a rotary valve can be dispensed with, thereby reducing losses and thus significantly increasing the efficiency of the compressor device.
  • such a compressor device can be designed to be more compact, since a single-cylinder structure of the compressor device is possible.
  • a further advantage of such a compressor device is that the reliability of the compressor device can be increased by reducing the number of assemblies.
  • the design of the compressor element as a metal bellows has the advantage over, for example, a design of the compressor element made of rubber that the working gas cannot escape from the compressor element or through the compressor element into the transmission space.
  • a volume of a space/fluid space enclosed by the piston, the compressor element and the cylinder may be constant.
  • an area of the transfer space outside the compressor element/the working space can be completely filled with the transfer fluid be, wherein the transfer fluid can be a substantially incompressible fluid.
  • the transmission space and the working space can be formed completely and without any protrusion in the cylinder.
  • a pressure of the working medium in the working space at any time may correspond to a pressure of the transfer fluid in the transfer space.
  • the pressure in the compressor element at any time corresponds to the pressure surrounding the compressor element.
  • the working medium in the working space and the transfer fluid in the transfer space are in a pressure equilibrium.
  • the compressor element itself does not experience or absorb large loads/forces and the compressor element can be designed to be thin-walled, which further reduces losses during compression of the compressor element.
  • the pressure of the working medium and the pressure of the transfer fluid may be greater than an ambient pressure of an environment surrounding the compressor device.
  • the compressor device is preloaded so that in every position of the piston in the cylinder there is an excess pressure of the working medium and the transmission medium relative to the environment.
  • a piston maximum stroke may be greater than a compressor element maximum stroke.
  • an amplitude that the piston performs during the periodic back and forth movement in a piston movement direction can be greater than a maximum change in a compressor element extension of the compressor element in the piston movement direction.
  • a lower compressor element maximum stroke can ensure that mechanical stress on the compressor element, especially in bends/folds of the compressor element, is kept low, which extends the service life of the compressor element and reduces the risk of failure.
  • the piston can be periodically movable back and forth by a connecting rod.
  • a connecting rod By using the connecting rod to move the piston, a conventional electric motor can be used as the driving means.
  • the piston can be movable back and forth by a threaded rod or the like.
  • the compressor element can be guided in a lifting direction.
  • the compressor device can include at least one guide element, which is designed to guide the compressor element during compression and expansion and to prevent the compressor element from buckling or collapsing in an uncontrolled manner.
  • the guide element can, for example, be rod-shaped or sleeve-shaped. More than one guide element can preferably be formed in the compressor device.
  • a closed displacer (pot element) can be formed in the working space.
  • the displacer element can be formed on an inside of the compressor element facing the working space, preferably on an end face of the compressor element close to the piston.
  • the displacement element can be a gas-tight, in particular cylindrical, element which can be designed to be firmly connected to the compressor element.
  • the gas volume of the working space can be reduced. This can ensure that the working space in the compressed state has a (dead/residual) volume of approximately zero, which reduces the deflection of the compressor element and thus the Load on the compressor element reduced.
  • a maximum longitudinal extent of the compressor element in the stroke direction in the expanded state may be more than twice as large as a minimum longitudinal extent in the stroke direction of the compressor element in the compressed state.
  • the transfer space and/or the working space can be connected to at least one expansion tank, optionally via a valve, in order to bias the compressor device and to compensate for any changes in volume, in particular when starting up or starting up the compressor device.
  • the compression of the compressor element is reversible. This means that the compressor element only has its geometry during operation a predefined frame and then regains an initial geometry.
  • a wall thickness of the compressor element can be constant.
  • the wall thickness of the compressor element can preferably be less than 0.2 mm.
  • the compressor element can be formed from a plurality of membrane pairs.
  • the compressor element can preferably be formed from at least 30 pairs of membranes.
  • the compressor element can be formed from at least 40 pairs of membranes.
  • each of the membrane pairs experiences only a small deflection during the stroke movement of the compressor element, which significantly reduces mechanical stress on the compressor element.
  • the transmission space can be designed with a multi-stage geometry, in particular a two-stage geometry.
  • the transmission space can have a jump in diameter, wherein a first diameter in a region of the piston can preferably be smaller than a second diameter in a region of the compressor element.
  • the drive device can be designed with a control device and/or connected to the control device, which controls the compression/compression and relaxation of the working medium in the working space via the periodic longitudinal movement of the piston, in particular via a speed of the drive device.
  • a displacement volume displaced by the piston during the movement of the piston can correspond to a change in the volume of the working space, whereby control of the compressor device is considerably simplified.
  • a filter can be connected downstream of the compressor device.
  • the working medium can be helium.
  • the movement profile of the piston is not a linear or sinusoidal profile, but follows a step function in which the working gas is compressed quickly, the pressure is maintained and then the working gas is quickly expanded again.
  • This movement profile can be achieved by a corresponding variable control of the drive device.
  • the drive device can be controlled uniformly and the jump function-shaped movement of the piston can be achieved by means of a corresponding transmission element, such as a cam.
  • a linear movement of the drive device can be translated into an almost jump function-shaped movement of the piston by a cam-shaped transmission element.
  • the transmission element can be asymmetrical to an axis of rotation of the transmission element.
  • the one drive device can drive more than one compressor device.
  • the cylinders can preferably be arranged in a boxer formation.
  • two cylinders can be designed diametrically opposite the drive device, whereby the cylinders can be constructed identically.
  • Each of the cylinders may be formed with a piston and a compressor element.
  • the transmission fluid may (also) be used as a lubricant for the drive device.
  • the transmission fluid can be formed as a lubricant on a side of the piston facing away from the transmission space.
  • the transmission fluid can lubricate an engine-connecting rod pairing and a connecting rod-piston pairing.
  • the compressor device can be designed for a working frequency range between 0.1 and 10 Hz and in particular for a working frequency range between 0.5 and 5 Hz.
  • the object is achieved by a cooling device with a compressor device according to one of the above aspects and a Gifford-McMahon cooler or a pulse tube cooler.
  • the cooling device includes a compressor device according to one of the above aspects and the Gifford-Mcmahon cooler or the pulse tube cooler connected via the connection.
  • a heat exchanger for cooling the working gas can be formed between the cooling device and the Gifford-McMahon cooler or the pulse tube cooler, or a cooling device can be formed directly on the Gifford-McMahon cooler or the pulse tube cooler.
  • the compressor device and the Gifford-McMahon cooler or the pulse tube cooler may be connected via a high pressure port.
  • the cooling device or the compressor device can be preloaded with 16 bar.
  • a working range of the compressor device can be between 8 bar and 24 bar.
  • a compressor refrigerator may be formed with a compressor device according to one of the above aspects, an evaporator and a condenser.
  • Fig. 1 is a schematic representation of a compressor device according to the invention in a general embodiment
  • Fig. 2 is a schematic representation of the compressor device according to the invention in a specific embodiment
  • Fig. 3 is a schematic representation of a structure of a cooling device according to the invention in a first embodiment
  • Fig. 4 is a schematic representation of a structure of the cooling device according to the invention in a second embodiment
  • Fig. 5 is a schematic representation of a compressor device according to the invention in a first alternative embodiment
  • Fig. 6 is a schematic representation of a compressor device according to the invention in a second alternative embodiment
  • Fig. 7 is a schematic representation of an inventive
  • FIG. 8 is a schematic representation of a compressor device according to the invention in a fourth alternative embodiment
  • Fig. 1 shows a compressor device 2 according to the invention with a gas-tight cylinder 4, a piston 6 arranged in the cylinder 4, a compressor element in the form of a (metal) bellows 8 and a connection 10, the compressor device 2 being provided and designed with a Cooling device to be coupled or to form part of the cooling device.
  • the cylinder 4 includes a (cylinder) running surface 12 formed on an inside of the cylinder 4.
  • the piston 6 includes a piston skirt 14 formed on an outer peripheral surface of the piston 6, the sound surface 12 of the cylinder 4 and the piston skirt 14 of the piston 6 being on top of each other in this way are coordinated so that the piston 6 is sealingly movable in the cylinder 4 linearly along a cylinder central axis ZM.
  • the piston 6 and the cylinder 4 delimit a transfer space 16.
  • the transfer space 16 is filled with a transfer fluid.
  • the bellows 8 is arranged in the transmission space 16 and surrounded by the (incompressible) transmission fluid. Specifically, the transfer fluid is formed in a fluid space 18 enclosed/enclosed between the cylinder 4, the piston 6 and the bellows 8.
  • a volume of the fluid space 18 is essentially unchangeable, although a geometry of the fluid space 18 can change.
  • the bellows 8 contains/delimits a working space 20.
  • the working space 20 is filled with a working gas, preferably helium.
  • the bellows 8 is designed as a folding bellows with an accordion-shaped wall 22.
  • the bellows 8 separates the transmission space 16 and the working space 20 from one another in a gas-tight and fluid-tight manner.
  • the connection 10 is formed on a side of the working space 20 facing away from the piston 6.
  • the connection 10 is provided and designed, the compressor device 2 with a cold head/cooler 38 (see Fig. 3), for example a Gifford-McMahon cooler or a pulse tube cooler.
  • Fig. 2 shows the compressor device 2 in an embodiment, wherein the piston 6 is linearly movable along the cylinder center axis ZM by means of a connecting rod 24.
  • a mode of operation of the compressor device 2 according to the invention is described below with reference to FIG. 2.
  • the drive of the piston 6 via the connecting rod 24 is exemplary.
  • other types of drive of the piston 6, which are suitable for periodically moving the piston 6 back and forth along the cylinder central axis ZM, are to be considered equivalent.
  • the connecting rod 24 is still mounted/fixed on the piston 6 at a second bearing point 32.
  • a rotary/circular movement of the disk 28 becomes a linear movement of the piston 6 along the cylinder central axis ZM.
  • a force generated by the electric motor 26 is transmitted to the piston 6 via the disk 28 and the connecting rod 24.
  • the force is transmitted to the transmission fluid in the fluid space 18.
  • the transmission fluid surrounding the bellows 8 transmits the force to the bellows 8 and compresses the working gas contained in the bellows 8. Since the transfer fluid is an approximately incompressible fluid, the force applied by the electric motor 26 (minus any friction losses) is essentially completely converted into a compression of the bellows 8 and the working gas located in the working space 20. In other words, the working gas in the working space 20 is periodically compressed by the force of the electric motor 26.
  • a working range of the bellows 8 lies between a first length L1 in the compressed state and a second length L2 in the relaxed state.
  • One (Maximum) change in length AL of the bellows 8, which corresponds to a difference between the first length L1 and the second length L2, is much smaller than the first length L1 or the second length L2.
  • Fig. 3 shows a cooling device 34 according to the invention with the compressor device 2 in a first embodiment.
  • the working space 20 of the compressor device 2 is connected to a pressure line 36 via the connection 10.
  • the pressure line 36 connects the compressor device 2 in a gas-tight manner with a cold head 38 designed as a Gifford-McMahon cooler or pulse tube cooler.
  • a specific working gas volume is periodically compressed and expanded by the compressor device 2 in a predetermined frequency range.
  • Fig. 4 shows the cooling device 34 according to the invention with the compressor device 2 in a second embodiment.
  • the cooling device 34 of the second embodiment essentially corresponds to the cooling device 34 of the first embodiment.
  • a heat exchanger 40 is formed between the connection 10 of the compressor device 2 and the cold head 38, which is provided and designed to cool down the working gas, in particular after compression.
  • the first alternative embodiment of the compressor device 2 shown in FIG. 5 contains a pot element 42 in the bellows 8.
  • the pot element 42 is formed on an end face of the bellows 8 facing the piston 6 in the working space 20.
  • the pot element 42 reduces a gas volume/internal volume of the working space 20.
  • the pot element 42 is sealed gas-tight from the working space 20.
  • Fig. 6 shows a second alternative embodiment of the compressor device 2 with a wave or rod-shaped guide element 44.
  • the rod-shaped guide element 44 is formed on the end face of the bellows 8 facing the piston 6 in the transmission space 16.
  • the rod-shaped guide element 44 extends away from the bellows 8 towards the piston 6 and is mounted in the piston 6.
  • the rod-shaped guide element 44 is guided or mounted linearly in the piston 6.
  • the rod-shaped guide element 44 is guided or mounted in a bushing in the piston 6.
  • more than one rod-shaped guide element 44 is formed on the bellows 8. The rod-shaped guide element 44 prevents the bellows 8 from tilting relative to the piston 6.
  • FIG. 7 shows a third alternative embodiment of the compressor device 2 with a flat guide element 46.
  • the flat guide element 46 is formed on the end face of the bellows 8 facing the piston 6 in the transmission space 16.
  • the flat guide element 46 extends radially outwards towards the running surface 12 and guides the bellows 8 relative to the running surface 12.
  • Bores 48 are formed in the flat guide element 46, which ensure unhindered flow of the transmission fluid in the transmission space.
  • the flat guide element 46 prevents the bellows 8 from tilting relative to the cylinder 4.
  • Fig. 8 shows a fourth alternative embodiment of the compressor device 2, wherein the cylinder 4 is designed in two stages.
  • the cylinder 4 includes a first cylinder section 50 in which the bellows 8 is formed and a second cylinder section 52 in which the piston 6 is formed.
  • a first diameter of the first cylinder section 50 is larger than a second diameter of the second cylinder section 52.
  • a pressure transmission in the cylinder 4 is implemented by the first cylinder section 50 and the second cylinder section 52.
  • the compression device 2 is formed with the pot element 42 in the working space 20 and the bellows 8 is also included the rod-shaped guide element 44 and / or the flat guide element 46 is formed.
  • the compression device 2 is designed with the cylinder 4, which has the first cylinder section 50 and the second cylinder section 52, and the pot element 42.
  • the compressor device is designed with the cylinder 4, which has the first cylinder section 50 and the second cylinder section 52, the pot element 42 and the rod-shaped guide element 44 and/or the flat guide element 46.

Landscapes

  • 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)

Abstract

La présente invention concerne un dispositif (2) de compresseur comportant un cylindre (4), un piston (6) qui est situé à l'intérieur du cylindre (4) et délimite un espace (16) de transfert rempli d'un fluide de transfert et qui peut être périodiquement animé d'un mouvement de va-et-vient au moyen d'un dispositif (26) d'entraînement, un élément (8) de compresseur, en particulier un soufflet (métallique), qui est disposé à l'intérieur de l'espace (16) de transfert et qui délimite un espace de travail/espace (20) de compression rempli d'un gaz de travail, et comportant un raccord (10) par l'intermédiaire duquel l'espace de travail (20) peut être relié à une canalisation (36) de gaz de travail vers un refroidisseur de Gifford-McMahon ou un refroidisseur (38) de type tube à pulsion, l'élément (8) de compresseur et le gaz de travail contenu dans celui-ci étant périodiquement comprimés indirectement par le biais du fluide de transfert qui est chassé par le piston (6).
PCT/EP2023/065892 2022-06-23 2023-06-14 Dispositif de compresseur, et dispositif de refroidissement doté d'un dispositif de compresseur WO2023247277A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102022115715.6 2022-06-23
DE102022115715.6A DE102022115715A1 (de) 2022-06-23 2022-06-23 Kompressorvorrichtung und Kühlvorrichtung mit Kompressorvorrichtung

Publications (1)

Publication Number Publication Date
WO2023247277A1 true WO2023247277A1 (fr) 2023-12-28

Family

ID=86895867

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2023/065892 WO2023247277A1 (fr) 2022-06-23 2023-06-14 Dispositif de compresseur, et dispositif de refroidissement doté d'un dispositif de compresseur

Country Status (2)

Country Link
DE (1) DE102022115715A1 (fr)
WO (1) WO2023247277A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE633104C (de) 1935-04-17 1936-07-20 Zehnder Radiatoren & Appbau Ge Kuehlschrank mit durch Wasserkraft angetriebenem Kaeltemittelkompressor
DE1403969A1 (de) * 1964-05-14 1968-11-21 Brown Boveri Krupp Reaktor Kompressor oder Vakuumpumpe
DE10137552C1 (de) 2001-08-01 2003-01-30 Karlsruhe Forschzent Einrichtung mit einem Kryogenerator zur Rekondensation von tiefsiedenden Gasen des aus einem Flüssiggas-Behälter verdampfenden Gases
DE102014217897A1 (de) * 2014-09-08 2016-03-10 Pressure Wave Systems Gmbh Kompressorvorrichtung, eine damit ausgerüstete Kühlvorrichtung und ein Verfahren zum Betreiben der Kompressorvorrichtung und der Kühlvorrichtung
US20160123313A1 (en) * 2014-11-05 2016-05-05 Simmons Development, Llc Pneumatically-operated fluid pump with amplified fluid pressure, and related methods

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1757168U (de) 1957-07-10 1957-12-05 Alfred Rossak Durch kolben-kraftmaschinen betaetigter impuls-kompressor fuer kleinkuehlanlagen.
JPH0781754B2 (ja) 1990-06-28 1995-09-06 新技術事業団 冷凍機
DE10336008A1 (de) 2003-08-01 2005-03-10 Werner Labs Fluidzylinder und Druckwandler
EP2710263B1 (fr) 2011-08-03 2016-09-14 Pressure Wave Systems GmbH Dispositif de compresseur
DE202012100995U1 (de) 2012-03-20 2013-07-01 Pressure Wave Systems Gmbh Kompressorvorrichtung
DE102012213293B4 (de) 2012-07-27 2018-03-29 Pressure Wave Systems Gmbh Kompressorvorrichtung sowie eine damit ausgerüstete Kühlvorrichtung und eine damit ausgerüstete Kältemaschine
ES2939370T3 (es) 2016-01-12 2023-04-21 Freezio Ag Sistema de dispensador con soporte para cartucho
WO2019048647A1 (fr) 2017-09-08 2019-03-14 Sera Gmbh Compresseur avec un soufflet à membrane métallique et procédé de fonctionnement d'un tel compresseur
DE102021002178A1 (de) 2021-04-24 2022-10-27 Hydac Technology Gmbh Fördereinrichtung

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE633104C (de) 1935-04-17 1936-07-20 Zehnder Radiatoren & Appbau Ge Kuehlschrank mit durch Wasserkraft angetriebenem Kaeltemittelkompressor
DE1403969A1 (de) * 1964-05-14 1968-11-21 Brown Boveri Krupp Reaktor Kompressor oder Vakuumpumpe
DE10137552C1 (de) 2001-08-01 2003-01-30 Karlsruhe Forschzent Einrichtung mit einem Kryogenerator zur Rekondensation von tiefsiedenden Gasen des aus einem Flüssiggas-Behälter verdampfenden Gases
DE102014217897A1 (de) * 2014-09-08 2016-03-10 Pressure Wave Systems Gmbh Kompressorvorrichtung, eine damit ausgerüstete Kühlvorrichtung und ein Verfahren zum Betreiben der Kompressorvorrichtung und der Kühlvorrichtung
US20160123313A1 (en) * 2014-11-05 2016-05-05 Simmons Development, Llc Pneumatically-operated fluid pump with amplified fluid pressure, and related methods

Also Published As

Publication number Publication date
DE102022115715A1 (de) 2023-12-28

Similar Documents

Publication Publication Date Title
DE2949792A1 (de) Kuehlsystem und kolbenverdichter mit druckstabilisierender dichtung
DE112010003623B4 (de) Lagerungssystem für freikolben-stirling maschinen
WO1997017546A1 (fr) Convertisseur pneumo-hydraulique pour accumuler l'energie
EP0422338B1 (fr) Amortisseur de vibrations à liquide
DE4219550A1 (de) Ausstroemdaempfer fuer einen kuehlungskompressor
EP2806164A1 (fr) Compresseur à spirale et installation de climatisation de véhicule à CO2 dotée d'un compresseur à spirale
DE19722688C2 (de) Kompressor
EP2806165B1 (fr) Compresseur à spirale et installation de climatisation de véhicule à CO2 dotée d'un compresseur à spirale
DE2262435C3 (de) Heißgasmotor mit zwei Zylindern und zwei Kolben
DE69908960T2 (de) Niederdruck- betätigungsglied
DE60202393T2 (de) Doppelkolbenpumpe
EP2710263B1 (fr) Dispositif de compresseur
EP3191712B1 (fr) Dispositif de compression, dispositif de refroidissement équipé de celui-ci et procédé pour faire fonctionner le dispositif de compression et le dispositif de refroidissement
WO2023247277A1 (fr) Dispositif de compresseur, et dispositif de refroidissement doté d'un dispositif de compresseur
EP2828524A1 (fr) Unité de compresseur, ainsi que compresseur
EP2877748B1 (fr) Dispositif compresseur ainsi qu'un dispositif de réfrigération ainsi équipé et une machine frigorifique ainsi équipée
DE102015213338A1 (de) Aktuatoreinheit
DE19841686C2 (de) Entspannungseinrichtung
DE10342421A1 (de) Tauchkolbenverdichter für Kältemittel
DE3444978A1 (de) Vorrichtung zur speicherung bzw. uebertragung von energie
DE102004056298B4 (de) Kombinierter Kolben-Expander-Verdichter
DE102016210728A1 (de) Förderpumpe für kryogene Kraftstoffe und Kraftstofffördersystem
EP2795204B1 (fr) Compresseur
EP3663579B1 (fr) Compresseur à piston
DE202012100995U1 (de) Kompressorvorrichtung

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 23732558

Country of ref document: EP

Kind code of ref document: A1