EP2122169A1 - Machine à fonctionnement fluidique - Google Patents

Machine à fonctionnement fluidique

Info

Publication number
EP2122169A1
EP2122169A1 EP07856620A EP07856620A EP2122169A1 EP 2122169 A1 EP2122169 A1 EP 2122169A1 EP 07856620 A EP07856620 A EP 07856620A EP 07856620 A EP07856620 A EP 07856620A EP 2122169 A1 EP2122169 A1 EP 2122169A1
Authority
EP
European Patent Office
Prior art keywords
piston
liquid
fluid
solid
machine according
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.)
Granted
Application number
EP07856620A
Other languages
German (de)
English (en)
Other versions
EP2122169B1 (fr
Inventor
Manfred Dehnen
Heiko Habel
Christopher Skamel
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.)
Andreas Hofer Hochdrucktechnik GmbH
Original Assignee
Andreas Hofer Hochdrucktechnik 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 Andreas Hofer Hochdrucktechnik GmbH filed Critical Andreas Hofer Hochdrucktechnik GmbH
Publication of EP2122169A1 publication Critical patent/EP2122169A1/fr
Application granted granted Critical
Publication of EP2122169B1 publication Critical patent/EP2122169B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • F04B35/045—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric using solenoids
    • 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
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F04B17/04—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
    • F04B17/042—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids the solenoid motor being separated from the fluid flow
    • F04B17/044—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids the solenoid motor being separated from the fluid flow using solenoids directly actuating the piston
    • 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
    • F04B25/00—Multi-stage pumps
    • F04B25/005—Multi-stage pumps with two cylinders
    • 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
    • F04B25/00—Multi-stage pumps
    • F04B25/02—Multi-stage pumps of stepped piston type
    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
    • F04B39/0011—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons liquid pistons
    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/06—Cooling; Heating; Prevention of freezing
    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/06—Cooling; Heating; Prevention of freezing
    • F04B39/064—Cooling by a cooling jacket in the pump casing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F1/00—Pumps using positively or negatively pressurised fluid medium acting directly on the liquid to be pumped
    • F04F1/06—Pumps using positively or negatively pressurised fluid medium acting directly on the liquid to be pumped the fluid medium acting on the surface of the liquid to be pumped

Definitions

  • the invention relates to a fluid working machine for compressing or conveying fluids, in particular for compressing gases to high pressures, with a linear motor, at least one cylinder, a solid piston movable axially in the cylinder or an axially movable liquid piston and at least one between the cylinder and the Solid piston or the liquid piston formed compression space, the linear motor transmits a translational driving force on the solid-state piston or the liquid piston.
  • Fluid power machines are known in various embodiments and variants of the prior art.
  • the fluid working machines can be subdivided first according to whether they are provided for conveying or compressing liquids or gases.
  • Fluid power machines used to convey fluids are also commonly referred to as pumps, while fluid power machines are referred to as compressors for compressing gases.
  • fluid working machines can also be distinguished according to the type of drive force - hydraulic, electrical or electro-magnetic - as well as the type of drive movement - rotational or translatory.
  • the present invention relates to a fluid working machine in which the driving force is generated by a linear motor which exerts a translational driving force on a piston guided in a cylinder directly, ie without converting a rotational movement via a gear. If a gas is to be compressed with such a fluid working machine, then the machine can also be referred to as a piston compressor or as a linear compressor.
  • the linear motor consists essentially of a stator or stator and a rotor or actuator, wherein the linear motor as well as a rotating motor may be formed as an asynchronous or synchronous linear motor.
  • the linear motor then corresponds to a developed asynchronous motor with a squirrel-cage rotor or a permanently excited synchronous motor, wherein a traveling field is generated by the coil or winding of the stator instead of a rotating field.
  • the power transmission takes place as in Three-phase machines either by voltage induction in the squirrel-cage rotor of the induction motor or by interaction with the field of permanent magnets of the synchronous motor.
  • a previously described linear compressor in which the magnet of the rotor is attached to a magnetic frame which is fixedly mounted on an end face of the piston.
  • a cooling channel is provided for cooling the linear motor, by which the coil of the stator mounted on a coil holder is cooled with a coolant.
  • a pump is provided which promotes oil within a hermetically sealing the linear compressor container through the cooling channel to the coil or the bobbin holder. The returning oil is collected in the lower part of the hermetically sealed container.
  • a compressor for a motor vehicle air conditioner with a closed refrigerant circuit which has a compressor housing with a compression space formed therein and a reciprocating in this reciprocating piston, in which as a drive for the compressor, a linear motor is used with variable drive frequency, is attached to the reaction part on the compressor chamber side end face of the reciprocating piston.
  • the well-known compressor is simple, consists of only a few components and is relatively small-sized. Storage, lubrication and sealing problems should not occur at any pressure level on the high pressure side between 80 and 160 bar.
  • the sealing of the reciprocating piston with respect to the compression space wall by means of conventional ring seals on the reciprocating piston. Since leakages to the atmosphere occur in principle in such moving seals, at least over time, the compressor known from DE 102 14 047 A1 is at least not suitable for compression to high pressures (> 150 bar) and is not provided.
  • a solid-state piston should be understood to mean (conventional) solid or solid (metal) pistons. as they have long been known.
  • the compressors described above have such solid-state pistons.
  • a liquid piston in the context of the invention should be understood to mean a liquid which, although liquid, behaves as a solid insofar as a compression of the gas is achieved by a change in the liquid level of the liquid. In this case, the liquid and the gas to be compressed are both in the cylinder, but without causing a mixing of liquid and gas.
  • the liquid piston or "liquid piston” thus assumes the function of the solid-state piston, the liquid piston as well as the solid-state piston being driven translationally by the traveling magnetic field of the linear motor generated by means of coils.
  • a fluid working machine with a liquid piston is known, for example, from DE 10 2004 046 316 A1, wherein in the compressor disclosed there, an ionic liquid is preferably used, so that the compressor is also referred to as an "ionic compressor".
  • the known compressor has two interconnected cylinders, in each of which a liquid and the gas to be compressed are located. By means of a hydraulic pump, the liquid levels in the two cylinders are varied so that one of the cylinders sucks the gas to be compressed, while in the other cylinder, a compression of the gas takes place.
  • the present invention has for its object to provide an initially described fluid working machine for compressing or conveying fluids available, the simplest possible structure a leakage and possibly also lubricant-free compression or delivery of fluids, in particular a compression of gases to high Pressures, allows.
  • this object is initially achieved in that the solid-body piston or the liquid piston in the region of the linear motor is enclosed by a fixed can.
  • the arrangement of a split tube can be achieved in a simple manner, the freedom from leaks to the atmosphere. By sealing the solid-state piston to the drive and thus the atmosphere of moving seals inherent leaks are by avoided the can.
  • the arrangement of the split tube can be sealed to the atmosphere only with static seals.
  • the can is arranged in the radial direction between the rotor and the coil of the stator, so that the can encloses the rotor.
  • the split tube is thus between the stator and the rotor.
  • both the rotor and the coil of the stator are arranged within the can, so that the can encloses the rotor and the stator.
  • the can thus serves as a partition between the electric drive system and the fluid-contacting compression chamber or the moving solid-state piston, wherein the can is penetrated by the magnetic field for energy transfer.
  • This disadvantage of greater losses does not occur in the second embodiment in which the can encloses the rotor and the stator.
  • This embodiment is thus - at least theoretically - advantageous unless it is to be compacted with the fluid handling machine aggressive media. In this case, the coil would also be exposed to the aggressive medium in the outer can, which can lead to a deterioration of the life of the coil.
  • the fluid working machine according to the invention can be advantageously constructed simply by the fact that the magnets of the rotor are arranged directly on the piston. By attaching the magnets of the rotor directly on the piston eliminates the formation and arrangement of a separate magnetic frame. In addition, this embodiment can reduce the radial dimensions of the fluid working machine, in particular of the cylinder.
  • the fluid-working machine is designed in multiple stages, ie the compression of a gas takes place in at least two, preferably in four stages. Alternatively, a single-stage compression is possible, in which case preferably a compensation stage is provided in order to keep the resulting forces necessary for compaction low. If the compression of the gas in several stages, it is advantageously provided that the solid-state piston has a plurality of sections with different diameters.
  • the piston can be composed manufacturing technology of several piston sections.
  • the compression chamber connected to the can is directly or via a conduit or a channel formed in the cylinder or in the housing with the fluid inlet side, d. H. connected to the suction side of the fluid work machine.
  • the pressure in the region of the can is reduced to the low pressure at the fluid inlet side.
  • Internal leaks that occur along the moving piston seals are released to the suction pressure and discharged to the fluid inlet side.
  • the required wall thickness of the split tube can be reduced, thereby reducing the electrical losses in an arrangement of the can between the rotor and the coil of the stator.
  • An otherwise required at particularly high pressures thick or double-walled design of the can can be eliminated. Irrespective of this, however, the use of a double-walled split tube is possible in order to increase safety, in particular in the case of particularly hazardous gases (toxic, polluting or radioactive gases).
  • the can it is also possible to make the can not made of metal but of a plastic or ceramic. When choosing the plastic or the ceramic care must be taken to ensure that the canned pipe can withstand the maximum occurring pressure safely.
  • a further embodiment of the invention is - as basically known in the art - at least one heat exchanger for return Cooling of the fluid provided.
  • a heat exchanger is preferably arranged after each compression stage.
  • the coolant required for the recooling of a gas through the heat exchanger can then preferably also be used for cooling the linear motor.
  • the cooling is preferably carried out from the outside, ie via a housing surrounding the linear motor, so that neither the rotor nor the stator comes directly into contact with the coolant.
  • the fluid itself can be used both for re-cooling the fluid and for cooling the linear motor, provided that the fluid is in a correspondingly cold state. If the gas to be compressed, for example hydrogen, is present in the liquid phase before deep-freezing, then the gas can be used as coolant in the liquid phase.
  • the liquid piston is preferably formed of a magnetizable liquid which has no vapor pressure, so that no molecules of the liquid mix with the gas to be compressed.
  • a liquid piston for example, an ionic liquid can be used. If such a liquid is used, which does not mix with the gas to be compressed, as long as its decomposition temperature is not reached, it can be dispensed with a subsequent separation of the liquid from the compressed gas.
  • the gap tube is preferably arranged in the radial direction within the coil of the stator, so that the gap tube surrounds the liquid acting as a rotor. In the area of the linear motor, the can thus has the function of the cylinder wall.
  • liquid piston instead of a solid-state piston, not only the use of the solid piston but also the otherwise required piston seals can be dispensed with.
  • the sealing of the compression space is carried out directly by the liquid piston forming liquid so that leakage to the atmosphere can not occur.
  • Piston seals also the maintenance of the fluid working machine, since no wearing parts are used within the working space.
  • the change in the liquid level is not by means of a hydraulic pump but by the linear motor, whose traveling magnetic field generated by the coils exerts a translational motive force on the magnetizable liquid.
  • a linear motor instead of a hydraulic pump, on the one hand, a higher maximum pressure of the gas to be compressed can be achieved, on the other hand, the wear occurring when using a hydraulic pump is avoided.
  • a liquid piston also has the advantage that over the liquid an at least partial discharge of the compression heat generated during compression and simultaneously cooling of the linear motor, in particular cooling of the coil of the stator, can take place.
  • at least one heat exchanger for recooling the liquid is preferably provided.
  • the above-described fluid working machine according to the invention is particularly suitable for the compression of gases to high pressures, in particular for the compression of hydrogen to 500 bar or more.
  • a linear compressor is particularly suitable for the equipment of water Stofftankstellen.
  • 1 shows a first embodiment of a fluid working machine according to the invention
  • 2 is an enlarged view of the portion A of the Fluidar- beitsmaschine of FIG. 1,
  • FIG. 3 shows a second exemplary embodiment of a fluid-assisting machine according to the invention
  • FIG. 4 is an enlarged view of a portion of the Fluidarbeits- machine according to FIG. 3,
  • Fig. 5 shows a third embodiment of a fluid-working machine according to the invention.
  • FIG. 6 shows a fourth exemplary embodiment of a fluid-operated machine according to the invention
  • FIGS. 1, 3, 5 and 6 show four different exemplary embodiments of a fluid working machine 1 according to the invention, wherein the figures are merely simplified representations, so that only the essential components for the present invention are shown.
  • the fluid working machines 1 shown in the figures serve to compress gases, in particular hydrogen, to a high pressure of, for example, 500 bar. Such fluid working machines 1 can therefore be used advantageously in particular for equipping hydrogen refueling stations.
  • the fluid working machines 1 shown in FIGS. 1, 3 and 5 each have a linear motor 2 for driving a solid-body piston 4 movably arranged in a cylinder 3.
  • a linear motor 2 for driving a solid-body piston 4 movably arranged in a cylinder 3.
  • a translatory drive force is exerted on the solid-state piston 4, so that the solid-state piston 4 can move axially back and forth within the cylinder 3, 3 * .
  • Within the cylinder 3 is at least one compression space 5, for the gas to be compressed, wherein the size of the compression space 5 changes depending on the position of the solid-state piston 4.
  • the fluid working machine 1 is a total of 4 stages, so that the compression of the Gas takes place in four successive stages. Accordingly, in these two embodiments, four sections 41, 42, 43, 44, each having different diameters, are formed on the solid-body piston 4. Correspondingly, the cylinder 3, 3 1 has four different sections with different inside diameters, so that a total of four compression spaces 5 are formed.
  • the fluid-working machine 1 according to FIG. 5 is designed to be single-stage, but here it is a double-acting fluid working machine 1, so that in each case a compression space 5 is formed on both sides of the solid-body piston 4.
  • the linear motor 2 illustrated in FIGS. 1 to 5 has a stator with a coil 9 and a rotor with a plurality of magnets 10, the magnets 10 being arranged directly on the solid-state piston 4.
  • the can 6 is arranged in the radial direction between the rotor, ie the magnet 10 and the coil 9 of the stator, so that the can 6 not only the solid-body piston 4 but also encloses the magnets 10 of the rotor.
  • the can 6 is thus between the stator and the rotor, so that the can 6 is penetrated by the magnetic field.
  • both the rotor that is, the magnets 10 and the coil 9 of the stator disposed within the can 6.
  • not only the magnets 10 but also the coil 9 are exposed to the fluid which, despite the piston seal 8, enters the cylinder interior 7 in the region of the can 6.
  • FIGS. 1, 3 and 5 it is indicated that the compression space 5 connected to the gap space 6 is connected via a line 11 to the fluid inlet side 12 of the fluid work machine 1.
  • the pressure in the cylinder interior 7 surrounded by the can 6 is reduced, whereby the can 6 in the embodiment according to FIGS. 1 and 2 or the coil 9 and the can 6 in the embodiment according to FIGS. 3 and 4 are not unnecessary be charged.
  • a correspondingly smaller wall thickness for the can 6 can be selected, which leads to a reduction of eddy current losses occurring in the can 6.
  • the compression space 5 connected to the gap space 6 may also be directly connected to the fluid entry side 12, that is, the fluid chamber 12 may be connected directly to the fluid inlet side 12. H. the fluid enters into the compression space 5 connected to the gap 6. If the fluid to be compressed has a low temperature, cooling of the linear motor 2 can take place simultaneously.
  • valves 13 which are arranged in the region of the individual compression chambers 5 and preferably formed as a plate valves.
  • FIGS. 1 and 3 it is further indicated that the individual compression chambers 5 are connected to one another via lines 14, wherein a heat exchanger 15 for recooling the compressed gas is provided in each of the individual lines 14.
  • the fluid working machine 1 has a coolant circuit 16 for cooling the coil 9 of the stator and thus for cooling the linear motor 2 in total. The cooling takes place from the outside, d. H. via a housing surrounding the coil 9 17, so that the coil 9 does not come into direct contact with the coolant. Both for re-cooling of the compressed gas in the heat exchangers 15 and for cooling the linear motor 2 while the same coolant can be used.
  • the illustrated embodiments of the fluid power machine 1 each have two cylinders 3, 3 ', wherein the linear motor 2 with the split tube 6 or the housing surrounding the linear motor 2 17 between the two cylinders 3, 3' is.
  • the sealing between the end faces of the two cylinders 3, 3 'and the corresponding end faces of the housing 17 takes place via static seals 18th
  • Figs. 3 and 4 is also still removable that the electrical leads 19 to the inside of the can 6 arranged stator with the help of pressure-tight cable glands 20 are leak-free to the terminal box 21, wherein the terminal box 21 pressure-tight cable glands 20, so that the obtained by the can 6 leakage freedom to atmosphere is not repealed by the connection of the required lines 19.
  • FIG. 6 an embodiment of a fluid working machine 1 is shown, which has a liquid piston 4 'instead of a solid piston.
  • the liquid piston 4 1 forming liquid is disposed within the formed from the two cylinders 3, 3 1 and the split tube 6 U-shaped housing. Above the liquid is in both cylinders 3, 3 1 each a compression space 5 for the gas to be compressed, wherein the size of the two compression spaces 5 in dependence on the liquid level of the liquid, ie, changes from the position of the liquid piston 4 '.
  • the fluid working machine 1 shown in FIG. 6, just like the fluid working machine 1 according to FIG. 5, has a one-stage design, which is also a double-acting fluid working machine 1, so that in each case a compression space 5 is formed on both sides of the liquid piston 4 ' is.
  • a valve 13 is arranged at the inlet or at the outlet, wherein the outlets of the two compression chambers 5 via lines 14, in each of which a heat exchanger 15 is arranged for recooling the compressed gas, are interconnected.
  • the linear motor 2 is arranged together with the can 6 or the housing surrounding the linear motor 2 17 between the two cylinders 3, 3 ', so that the can 6 in the region of the linear motor 2, the cylinder wall for the liquid.
  • the fluid working machines 1 shown in the figures are particularly suitable for compressing gases, preferably hydrogen, to high pressures of, for example, 1000 bar, so that such fluid working machines 1 are particularly suitable for equipping hydrogen refueling stations.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Reciprocating Pumps (AREA)
  • Electromagnetic Pumps, Or The Like (AREA)
  • Linear Motors (AREA)

Abstract

La machine à fonctionnement fluidique représentée et décrite permet d'étanchéiser et/ou d'acheminer des fluides, en particulier étanchéiser des gaz à hautes pressions. Ladite machine comprend un moteur linéaire (2), au moins un cylindre (3), un piston à corps solide (4) pouvant se déplacer axialement dans le cylindre (3) ou un piston à corps liquide (4') pouvant se déplacer axialement et au moins une chambre de compression (5) conçue entre le cylindre (3) et le piston à corps solide (4) ou le piston à corps liquide (4'), le moteur linéaire (2) transmettant une force d'entraînement de translation sur le piston à corps solide (4) ou le piston à corps liquide (4'). Sur une telle machine à fonctionnement fluidique, une étanchéité ou un acheminement des fluides sans fuite et sans moyen de lubrification, en particulier une étanchéité de gaz à hautes pressions, est rendu possible avec une construction la plus simple possible par le fait que le piston à corps solide (4) ou le piston à corps liquide (4') est entouré dans la zone du moteur linéaire (2) par une gaine de moteur (6) disposée de manière fixe.
EP07856620.5A 2006-12-18 2007-12-12 Machine à fonctionnement fluidique Active EP2122169B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006060147A DE102006060147B4 (de) 2006-12-18 2006-12-18 Fluidarbeitsmaschine
PCT/EP2007/010872 WO2008074428A1 (fr) 2006-12-18 2007-12-12 Machine à fonctionnement fluidique

Publications (2)

Publication Number Publication Date
EP2122169A1 true EP2122169A1 (fr) 2009-11-25
EP2122169B1 EP2122169B1 (fr) 2015-09-23

Family

ID=39124605

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07856620.5A Active EP2122169B1 (fr) 2006-12-18 2007-12-12 Machine à fonctionnement fluidique

Country Status (5)

Country Link
US (1) US20110052430A1 (fr)
EP (1) EP2122169B1 (fr)
JP (2) JP5431953B2 (fr)
DE (1) DE102006060147B4 (fr)
WO (1) WO2008074428A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012016222A1 (de) 2012-08-01 2014-02-06 Technische Universität Dresden Kontinuierlich arbeitende Fluidarbeitsmaschine

Families Citing this family (32)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008036528A1 (de) * 2008-08-06 2010-02-11 Bentec Gmbh Drilling & Oilfield Systems Verfahren zum Betrieb einer mehrpulsigen Kolbenpumpe, mehrpulsige Kolbenpumpe sowie Herstellung einer solchen
DE102008060659A1 (de) 2008-12-08 2010-06-10 Bentec Gmbh Drilling & Oilfield Systems Klemmvorrichtung für Zylinderbuchsen sowie deren Verwendung und Spülpumpe mit Klemmvorrichtung
JP5377162B2 (ja) * 2009-08-28 2013-12-25 有限会社いどや 電磁ポンプ及び此れを用いた電磁ポンプシステム
US20110192573A1 (en) 2010-02-08 2011-08-11 Harmel Defretin System and method for moving a first fluid using a second fluid
DE102010053091A1 (de) * 2010-12-01 2012-06-06 Linde Aktiengesellschaft Mehrstufiger Kolbenverdichter
DE102012008811A1 (de) 2012-04-25 2013-10-31 Bpg Beteiligungs Gmbh Wärmekraftmaschine
CN103670996B (zh) * 2012-09-14 2016-02-10 胜瑞兰工业设备（苏州）有限公司 一种无泄漏式磁力驱动往复泵
EP2725227B1 (fr) * 2012-10-24 2015-05-20 Delphi International Operations Luxembourg S.à r.l. Ensemble de pompe
JP6087713B2 (ja) 2013-04-24 2017-03-01 株式会社神戸製鋼所 圧縮装置
US10323628B2 (en) * 2013-11-07 2019-06-18 Gas Technology Institute Free piston linear motor compressor and associated systems of operation
US11466678B2 (en) * 2013-11-07 2022-10-11 Gas Technology Institute Free piston linear motor compressor and associated systems of operation
DE102013019499A1 (de) 2013-11-21 2015-05-21 Linde Aktiengesellschaft Kolbenverdichter und Verfahren zum Verdichten eines tiefkalten, gasförmigen Mediums, insbesondere Wasserstoff
JP6163646B2 (ja) * 2014-05-27 2017-07-19 株式会社国際電気通信基礎技術研究所 アクチュエータ装置、ヒューマノイド型ロボットおよびパワーアシスト装置
JP6035590B2 (ja) * 2014-05-27 2016-11-30 株式会社国際電気通信基礎技術研究所 アクチュエータ装置、ヒューマノイド型ロボットおよびパワーアシスト装置
JP6276120B2 (ja) * 2014-06-27 2018-02-07 株式会社神戸製鋼所 ガス圧縮装置
DE102014012977A1 (de) * 2014-09-08 2016-03-10 Albonair Gmbh Reduktionsmitteldosiersystem mit verbesserter Förderpumpe
JP6276154B2 (ja) * 2014-09-26 2018-02-07 株式会社神戸製鋼所 往復動型圧縮装置
JP2016213314A (ja) * 2015-05-08 2016-12-15 富士通株式会社 冷却モジュール及び電子機器
DE102015209728A1 (de) * 2015-05-27 2016-12-01 Robert Bosch Gmbh Pumpeneinrichtung, Bremssystem
CN105443977B (zh) * 2015-12-28 2017-12-26 重庆耐德能源装备集成有限公司 天然气内冷式液力增压容器
US11118578B2 (en) * 2017-02-15 2021-09-14 Extiel Holdings, Llc Internally cooled inline drive compressor
CN107605691B (zh) * 2017-09-08 2019-04-02 中国神华能源股份有限公司 直线驱动柱塞泵、直线驱动乳化液泵系统、及控制方法
EP3698046B1 (fr) * 2017-10-17 2023-04-19 Gas Technology Institute Compresseur à moteur linéaire à piston libre et systèmes de fonctionnement associés
PL240516B1 (pl) * 2018-01-09 2022-04-19 Dobrianski Jurij Maszyna parowa
BE1026883B1 (nl) * 2018-12-18 2020-07-22 Atlas Copco Airpower Nv Zuigercompressor en werkwijze waarin zulke zuigercompressor wordt toegepast
BE1026881B1 (nl) * 2018-12-18 2020-07-22 Atlas Copco Airpower Nv Zuigercompressor
JP7330088B2 (ja) * 2019-12-16 2023-08-21 株式会社東芝 液体ピストン装置および液体ピストン動作方法
KR102712437B1 (ko) * 2022-01-19 2024-10-02 주식회사 에스씨에스 리니어 피스톤이 설치된 리니어 압축기용 실린더장치
CN115059597B (zh) * 2022-07-06 2025-07-25 九江市浩轩新能源开发有限公司 一种电磁液压泵站
IT202400000720A1 (it) * 2024-01-16 2025-07-16 Bosch Gmbh Robert Compressore alternativo
CN119727286B (zh) * 2025-02-28 2025-06-24 德瑞精工（深圳）有限公司 一种全密闭式直线电机模组
KR102866556B1 (ko) 2025-06-23 2025-10-01 주식회사 티이씨 직렬 다중 솔레노이드로 구동되는 이온성 액체 피스톤을 이용한 기체 압축기 및 그 제어방법

Family Cites Families (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3196797A (en) * 1961-09-18 1965-07-27 Mario Pagano S P A Dynamic thrust electromagnetic compressor, particularly suitable for compressing liquid or gaseous substances
DE2937157C2 (de) * 1979-09-13 1982-06-16 Franz Klaus Union Armaturen, Pumpen Gmbh & Co, 4630 Bochum Kolbenverdrängerpumpe, insbesondere Dosierpumpe
US4496287A (en) * 1980-02-14 1985-01-29 Robert M. Nelson Sensors for detection of fluid condition, and control systems utilizing their signals
NL8204005A (nl) * 1982-10-18 1984-05-16 Philips Nv Koelsysteem met twee-traps compressie-inrichting.
JPS60125371U (ja) * 1984-02-03 1985-08-23 三菱重工業株式会社 容積形ポンプまたはブロワ−
US4815949A (en) * 1985-06-24 1989-03-28 Rabson Thomas A In-well submersible motor with stacked component stator
US5354185A (en) * 1992-10-05 1994-10-11 Aura Systems, Inc. Electromagnetically actuated reciprocating compressor driver
EP1020013B1 (fr) * 1997-10-04 2004-04-28 Z & D Limited Compresseur a moteur lineaire
DE19846711C2 (de) * 1998-10-09 2003-05-08 Trumpf Sachsen Gmbh Hochdruckpumpe mit Linearmotorantrieb
US6183206B1 (en) * 1999-05-10 2001-02-06 The United States Of America As Represented By The Secretary Of The Air Force Magnetohydrodynamically-driven compressor
DE10149506A1 (de) * 2001-10-06 2003-04-10 Leybold Vakuum Gmbh Schwingkolbenantrieb für eine Vakuumpumpe sowie Betriebsverfahren für diesen Antrieb
DE10214047A1 (de) * 2002-03-28 2003-10-09 Volkswagen Ag Kompressor für eine Fahrzeugklimaanlage
DE10314007A1 (de) * 2003-03-28 2004-10-07 Leybold Vakuum Gmbh Steuerung einer Kolbenvakuumpumpe
JP2005307796A (ja) * 2004-04-20 2005-11-04 Matsushita Electric Ind Co Ltd リニア圧縮機
JP2005351255A (ja) * 2004-06-10 2005-12-22 Kaken Geneqs:Kk レシプロ圧縮機
DE102004046316A1 (de) * 2004-09-24 2006-03-30 Linde Ag Verfahren und Vorrichtung zum Verdichten eines gasförmigen Mediums
KR100613514B1 (ko) * 2004-10-07 2006-08-17 엘지전자 주식회사 리니어 압축기의 토출부 구조
DE102004055924B4 (de) * 2004-11-19 2011-08-18 Lg Electronics Inc., Seoul Linearkompressor
EP1785625A3 (fr) * 2005-11-10 2009-11-25 LG Electronics Inc. Compresseur linéaire

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2008074428A1 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012016222A1 (de) 2012-08-01 2014-02-06 Technische Universität Dresden Kontinuierlich arbeitende Fluidarbeitsmaschine

Also Published As

Publication number Publication date
US20110052430A1 (en) 2011-03-03
JP2014090663A (ja) 2014-05-15
EP2122169B1 (fr) 2015-09-23
JP5431953B2 (ja) 2014-03-05
WO2008074428A1 (fr) 2008-06-26
JP5868382B2 (ja) 2016-02-24
DE102006060147A1 (de) 2008-06-19
DE102006060147B4 (de) 2009-05-14
JP2010513779A (ja) 2010-04-30

Similar Documents

Publication Publication Date Title
EP2122169B1 (fr) Machine à fonctionnement fluidique
EP1999375B1 (fr) Unité de compression
EP1069313B1 (fr) Turbo-compresseur
WO2007110275A1 (fr) Unité de compresseur
EP3504433B1 (fr) Ensemble motopompe
DE3621027A1 (de) Drehkompressor
EP2806164B1 (fr) Compresseur à spirale et installation de climatisation de véhicule à CO2 dotée d'un compresseur à spirale
EP3523537A1 (fr) Compresseur frigorifique semi-hermétique
DE102010064061A1 (de) Turboverdichter und Verfahren zur Verdichtung von Gas
DE102011077096A1 (de) Pendelschieberpumpe
DE2621303A1 (de) Vorrichtung zur kompression und expansion von gas
DE29519941U1 (de) Hydraulisches Pumpenaggregat
EP2052158A1 (fr) Refroidissement de rotor pour pompes à vide ou compresseurs à deux arbres fonctionnant à sec
WO2020094510A1 (fr) Machine électrique comprenant un dispositif de refroidissement à fluide
EP2226920A2 (fr) Système de cogénération avec un moteur à combustion à piston et une machine électrique
WO2010084002A2 (fr) Ensemble machine hydraulique
DE3814269A1 (de) Kolbenmaschine
DE10349752B4 (de) Motorpumpenaggregat
EP2473739A2 (fr) Pompe à vis sèche à compression interne
DE3248229C1 (de) Arbeitsmaschine zum Fördern von Gasen und/oder Flüssigkeiten
WO2016193262A1 (fr) Pompe filtrante hydraulique électrique et pompe volumétrique hydraulique électrique à utiliser dans une pompe filtrante hydraulique
DE102021207660A1 (de) Linearverdichter
DE102020103384A1 (de) Schraubenverdichter mit einseitig gelagerten Rotoren
DE102013211185A1 (de) Spindelverdichter-Gehäuse
DE19948443A1 (de) Plungerpumpenaggregat, vorzugsweise für hohe Betriebsdrücke (II)

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20090715

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR

DAX Request for extension of the european patent (deleted)
17Q First examination report despatched

Effective date: 20100301

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20150330

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 751404

Country of ref document: AT

Kind code of ref document: T

Effective date: 20151015

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502007014253

Country of ref document: DE

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 9

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150923

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151224

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150923

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150923

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

REG Reference to a national code

Ref country code: NL

Ref legal event code: FP

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150923

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150923

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150923

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160123

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150923

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150923

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150923

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150923

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20151231

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160125

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502007014253

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151212

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150923

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20151223

26N No opposition filed

Effective date: 20160624

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150923

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20151223

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20151212

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150923

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 10

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20071212

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150923

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150923

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150923

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150923

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 11

REG Reference to a national code

Ref country code: CH

Ref legal event code: U11

Free format text: ST27 STATUS EVENT CODE: U-0-0-U10-U11 (AS PROVIDED BY THE NATIONAL OFFICE)

Effective date: 20260101

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 20251222

Year of fee payment: 19

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20251223

Year of fee payment: 19

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20251222

Year of fee payment: 19

Ref country code: NL

Payment date: 20251219

Year of fee payment: 19

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20260217

Year of fee payment: 19

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 20260101

Year of fee payment: 19