WO2016202443A1 - Procédé pour comprimer un gaz, unité de calcul et compresseur à piston polyétagé - Google Patents

Procédé pour comprimer un gaz, unité de calcul et compresseur à piston polyétagé Download PDF

Info

Publication number
WO2016202443A1
WO2016202443A1 PCT/EP2016/000973 EP2016000973W WO2016202443A1 WO 2016202443 A1 WO2016202443 A1 WO 2016202443A1 EP 2016000973 W EP2016000973 W EP 2016000973W WO 2016202443 A1 WO2016202443 A1 WO 2016202443A1
Authority
WO
WIPO (PCT)
Prior art keywords
compression stage
stage
compression
valve
pressure
Prior art date
Application number
PCT/EP2016/000973
Other languages
German (de)
English (en)
Inventor
Robert Adler
Sascha Dorner
Markus Stephan
Christoph Nagl
Original Assignee
Linde Aktiengesellschaft
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 Linde Aktiengesellschaft filed Critical Linde Aktiengesellschaft
Priority to EP16728839.8A priority Critical patent/EP3311028B1/fr
Priority to US15/580,433 priority patent/US20180180039A1/en
Publication of WO2016202443A1 publication Critical patent/WO2016202443A1/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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/24—Bypassing
    • 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
    • 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
    • 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
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/02—Stopping, starting, unloading or idling control
    • F04B49/022—Stopping, starting, unloading or idling control by means of 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/02—Stopping, starting, unloading or idling control
    • F04B49/03—Stopping, starting, unloading or idling control by means of valves
    • F04B49/035—Bypassing
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/225—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening
    • 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
    • F04B2205/00—Fluid parameters
    • F04B2205/01—Pressure before the pump inlet

Definitions

  • the invention relates to a method for compressing a gas by means of a multi-stage piston compressor, a computing unit for its implementation and such a multi-stage piston compressor.
  • Reciprocating compressors rotary compressors or ionic compressors are used.
  • For higher compression ratios can, for example, a multi-stage construction of
  • Compression devices are used. Individual stages are included.
  • valves or slider controls usually separated by valves or slider controls.
  • Such compaction devices or compressors are both power and power usually designed for defined sizes such as pressures, piston diameter and thus also gas forces. Changing these parameters on existing systems is therefore often difficult to achieve.
  • Compressors with linear motors in particular electric linear motors as a drive, can be designed in terms of force so that the pressure force of the individual
  • Compressor levels is higher than the achievable by the linear motor maximum force.
  • An inventive method is used for compressing a gas by means of a multi-stage piston compressor.
  • the gas is branched off at least partially, in particular completely, before the first compression stage and fed to a second compression stage immediately following the first compression stage.
  • the compression level does not have to be switched off. Instead, the branched off gas is fed directly to the subsequent compression stage. Since this compression stage is designed for higher input pressures, the gas can be compressed here. Thus, it is also possible to use a compressor for higher than actually provided input pressures. This may result in additional applications for a compressor, for which previously a larger or
  • a stroke of the piston of the piston compressor assigned to the first compression stage is reduced.
  • a dead space in the first compression stage can be deliberately allowed to increase the amount of gas in the corresponding cylinder.
  • it can be prevented that in the first
  • Compression level too low a cylinder pressure is created (the compression device pushes gas with a closed suction valve through a pressure valve, the gas but can not flow and the remaining gas is expanded, whereby a pressure drop occurs in the cylinder), which could, for example, lead to shutdown, otherwise air would be sucked from the outside and would mix with the gas to be compressed. In addition, this can reduce the power requirement of the compressor.
  • the stroke is reduced as a function of a residual pressure after a re-expansion in the first compression stage and / or an inlet pressure of the second compression stage.
  • the higher the residual pressure after the re-expansion in the first compression stage and / or the greater (in terms of the lift reduction) the input pressure of the second compression stage the further reduced a difference amount by which the stroke is reduced.
  • the dead volume of the relevant cylinder of the first compression stage can be taken into account. In this way, the operation of the compressor can be optimally adapted to the present circumstances.
  • the reduction of the stroke is determined on the basis of stored values for the residual pressure and / or the inlet pressure of the second compression stage.
  • the computational effort, especially in real time can be significantly reduced.
  • the values for the stroke reduction can be stored in accordance with increments of 0.5 bar of the respective pressures, for example in a control unit for the compressor.
  • the gas is branched off before the first compression stage and supplied to the second compression stage by a first valve in a first
  • Delivery path to the first compression stage at least partially closed and a second valve in a second conveying path from the first conveying path to the second compression stage is at least partially opened.
  • a valve logic with a second delivery path in the sense of a bypass line allows a particularly simple embodiment of the method.
  • an inlet valve of the first compression stage is used as the first valve.
  • the inlet valve can be locked, for example. In this way, except the second valve in the second conveying path, no additional valve is needed.
  • An arithmetic unit according to the invention is set up to carry out a method according to the invention.
  • a computing unit may, for example, be a programmable logic controller (PLC).
  • PLC programmable logic controller
  • a method and a device for knock detection is additionally provided.
  • An inventive multi-stage reciprocating compressor has a gas inlet, a first compression stage and a second compression stage.
  • a first valve is arranged in a first conveying path to a gas inlet of the first compression stage, and a second conveying path, which branches off from the first conveying path upstream of the first valve and leads to a gas inlet of the second compression stage, is provided.
  • a second valve is provided in the second conveying path.
  • the first valve is designed as an inlet valve of the first compression stage.
  • the multistage reciprocating compressor has at least one electric linear motor for moving pistons of the reciprocating compressor.
  • the multistage reciprocating compressor has an arithmetic unit according to the invention.
  • the reciprocating compressor is used for the compression of gases.
  • the reciprocating compressor is used for the compression of carbon dioxide, hydrogen, methane, natural gas, helium or nitrogen.
  • the reciprocating compressor for compressing gas is preferably operated at temperatures of -253 to 150 ° C.
  • the gas can preferably be compressed to pressures between 0.1 bar and 1000 bar.
  • the temperatures and pressures depend on the gas to be compressed.
  • gases may also be moist and / or contaminated gases or gas mixtures.
  • the inlet temperature (temperature before compression) of the carbon dioxide is preferably between -60 ° C and 120 ° C, especially 1 to 80 ° C.
  • Starting temperature (temperature after compression) of the carbon dioxide is preferably between 40 and 150 ° C, in particular between 60 and 100 ° C.
  • the inlet pressure (pressure before compression) of the carbon dioxide is preferably 0.1 bar to 10 bar, in particular 0.2 to 4 bar.
  • the initial pressure (pressure after compression) of the carbon dioxide is preferably between 5 and 100 bar, in particular 20 to 60 bar.
  • the volume flow is preferably 0.5 Nm 3 / h to 50 Nm 3 / h, in particular 1 Nm 3 / h to 8 Nm 3 / h. Hydrogen:
  • the inlet temperature (temperature before compression) of the hydrogen is preferably between -253 ° C and 80 ° C, especially -253 ° C to -80 ° C when used as a cryogenic compressor or in particular -20 ° C to 80 ° C in the Use as ionic compressor.
  • the starting temperature (temperature after compression) of the hydrogen is preferably between -250 and 150 ° C, especially between -60 and 80 ° C.
  • the inlet pressure (pressure before compression) of the hydrogen is preferably 0.8 bar to 40 bar, in particular 2.5 to 30 bar.
  • the outlet pressure (pressure after compression) of the hydrogen is preferably between 10 and 1000 bar, in particular 500 to 1000 bar.
  • the volume flow is preferably 0.5 Nm 3 / h to 500 Nm 3 / h, in particular at 50 Nm 3 / h to 350 Nm 3 / h.
  • Methane or natural gas Methane or natural gas
  • the inlet temperature (temperature before compression) of the methane or natural gas is preferably between -182 ° C and 80 ° C, especially -182 ° C to -40 ° C when used as a cryogenic compressor or more particularly -20 ° C to 80 ° C. when used as ionic compressor.
  • the starting temperature (temperature after compression) of the methane or natural gas is preferably between -180 and 150 ° C, in particular between -60 and 80 ° C.
  • the inlet pressure (pressure before compression) of the methane or natural gas is preferably 0.8 bar to 30 bar, in particular 1.5 to 20 bar.
  • the outlet pressure (pressure after compression) of the methane or natural gas is preferably between 10 and 650 bar, in particular 300 to 600 bar.
  • the volume flow is preferably 0.5 Nm 3 / h to 1000 Nm 3 / h, in particular at 5 Nm 3 / h to 350 Nn Vh.
  • Helium is preferably 0.5 Nm 3 / h to 1000
  • the inlet temperature (temperature before compression) of the helium is preferably between -269 ° C and 80 ° C, in particular -269 ° C to -80 ° C when used as a cryogenic compressor or especially -20 ° C to 80 ° C in the Use as ionic compressor.
  • the starting temperature (temperature after compression) of the helium is preferably between -269 and 150 ° C, in particular between -60 and 80 ° C.
  • the inlet pressure (pressure before compression) of the helium is preferably 0.8 bar to 40 bar, in particular 2.5 to 20 bar.
  • the initial pressure (pressure after compression) of the helium is preferably between 10 and
  • the volume flow is preferably 0.5 Nm 3 / h to 600 Nm 3 / h, in particular at 50 Nm 3 / h to 400 Nm 3 / h.
  • the inlet temperature (temperature before compression) of the nitrogen is preferably between -196 ° C and 80 ° C, in particular -196 ° C to -40 ° C when used as a cryogenic compressor or in particular -20 ° C to 80 ° C in the Use as ionic compressor.
  • the starting temperature (temperature after compression) of the nitrogen is preferably between -195 and 150 ° C,
  • the inlet pressure (pressure before compression) of the nitrogen is preferably 0.8 bar to 30 bar, in particular 1.5 to 17 bar.
  • the outlet pressure (pressure after compression) of the nitrogen is preferably between 10 and 650 bar, in particular 200 to 400 bar.
  • the volume flow is preferably 0.5 Nm 3 / h to 500 Nm 3 / h, in particular at 5 Nm 3 / h to 350 Nm 3 / h.
  • FIG. 1 shows a schematic diagram of a flowchart according to the invention
  • FIG. 2 shows a schematic diagram of stroke profiles in a diagram
  • Multi-stage reciprocating compressor according to the invention in a preferred embodiment.
  • FIG. 1 shows schematically and as a flow chart an inventive multistage reciprocating compressor 100 in a preferred embodiment.
  • Piston compressor 100 has a first compression stage 110 and a second compression stage 120.
  • the two compression stages are each designed as pistons that move in a cylinder. These pistons are driven by a linear electric motor 130. Of course, further compression stages can be provided.
  • the first compression stage has an inlet valve 111 and an outlet valve 112, which may be designed as pressure-controlled check valves.
  • the second compression stage 120 has an inlet valve 121 and an outlet valve 122, which may also be designed as pressure-controlled check valves.
  • the regular gas flow takes place via a first conveying path 161 (shown on the left in FIG. 1) to the first compression stage 110 and from the first compression stage 110 then to the second compression stage 120. Subsequently, the gas can be fed to a desired use.
  • pressure sensors 141, 142 and 143 are provided. With the pressure sensor 141, an input pressure to the first compression stage can be detected, with the pressure sensor 142, an output pressure of the first compression stage 110, respectively input pressure of the second compressor stage 120 can be detected and with the pressure sensor 143, an output pressure of the second compression stage 120 can be detected.
  • the pressure sensors 141, 142 and 143 are connected to a
  • PLC Programmable logic controller
  • a first valve 151 is provided in the first delivery path 161.
  • this first valve 151 can be actuated via the SPS 170, i. be opened and closed.
  • the first valve 151 is open in normal operation.
  • a second conveying path 162 is provided in the sense of a bypass line, which branches off from the first conveying path 161, specifically before the first valve 151, and leads in front of the second compression stage 120.
  • a second valve 152 is provided, which is also controlled by the SPS 170, i. can be opened and closed. In this case, the second valve 152 is in
  • This threshold can preferably be chosen so that with
  • Input pressures up to this threshold the power or the applicable force of the electric linear motor 130 for the first compression stage 110 just enough to perform the required compression. That way Incoming pressures at which the required compression could not be performed in the first compression stage 110 avoided.
  • the electric linear motor 130 is controlled by the SPS 170 in such a way that the stroke of the piston assigned to the first compression stage 110 is reduced.
  • Multi-stage reciprocating compressor according to the invention in a preferred
  • a stroke h is plotted against a time t.
  • h 2 is a stroke course of the piston assigned to the second compression stage.
  • the stroke hh of the piston of the first compression stage is now reduced by an amount Ah, so that there is a stroke h'-, for the piston of the first compression stage.
  • the stroke of the piston of the second compression stage remains unchanged. As already mentioned, a negative pressure in the second compression stage is thereby avoided.
  • p1 denotes the residual pressure after the re-expansion in the first
  • the pressure p1 can be a freely definable pressure that a
  • the pressure after the re-expansion may, for example, be calculated or determined indirectly, provided that the pressure p1 in the period of the re-expansion falls below the pressure measured by the pressure sensor 141. In this Case would gas from the volume between the valves 151, 1 1 1 and the
  • Pressure sensor 141 flow and the pressure measured by the pressure sensor 141 would thus drop.
  • p 2 the input pressure of the second compression stage, as it is measured, for example, by means of the pressure sensor 142, designated.
  • K is the isentropic coefficient of the adiabatic change of state and V sta t is a static dead volume of the first compression stage, as it results from the dimensions of the piston and the cylinder. With d is finally the

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)
  • Control Of Positive-Displacement Pumps (AREA)

Abstract

La présente invention concerne un procédé pour comprimer un gaz au moyen d'un compresseur à piston polyétagé (100). Selon l'invention, lorsqu'une pression d'entrée d'un premier étage de compression (110) dépasse une valeur seuil, le gaz est dévié au moins partiellement, notamment en intégralité, du premier étage de compression (110) et alimente un deuxième étage de compression (120) succédant directement au premier étage de compression (110). L'invention concerne également une unité de calcul pour mettre en œuvre le procédé et un compresseur à piston polyétagé (100) correspondant.
PCT/EP2016/000973 2015-06-16 2016-06-11 Procédé pour comprimer un gaz, unité de calcul et compresseur à piston polyétagé WO2016202443A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP16728839.8A EP3311028B1 (fr) 2015-06-16 2016-06-11 Procédé pour comprimer un gaz, unité de calcul et compresseur à piston polyétagé
US15/580,433 US20180180039A1 (en) 2015-06-16 2016-06-11 Method for compressing a gas, computing unit and multi-stage piston compressor

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015007731.7A DE102015007731A1 (de) 2015-06-16 2015-06-16 Verfahren zum Verdichten eines Gases, Recheneinheit und mehrstufiger Kolbenverdichter
DE102015007731.7 2015-06-16

Publications (1)

Publication Number Publication Date
WO2016202443A1 true WO2016202443A1 (fr) 2016-12-22

Family

ID=56121020

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2016/000973 WO2016202443A1 (fr) 2015-06-16 2016-06-11 Procédé pour comprimer un gaz, unité de calcul et compresseur à piston polyétagé

Country Status (4)

Country Link
US (1) US20180180039A1 (fr)
EP (1) EP3311028B1 (fr)
DE (1) DE102015007731A1 (fr)
WO (1) WO2016202443A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108548624A (zh) * 2018-04-12 2018-09-18 海信（山东）空调有限公司 用于压缩机配管的残余应力测试方法
CN113533600B (zh) * 2021-08-09 2022-02-22 江苏鑫华半导体材料科技有限公司 一种三氯硅烷的检测前处理方法及检测方法

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4236876A (en) * 1979-07-30 1980-12-02 Carrier Corporation Multiple compressor system
US5797729A (en) * 1996-02-16 1998-08-25 Aspen Systems, Inc. Controlling multiple variable speed compressors
WO2009058356A1 (fr) * 2007-11-02 2009-05-07 Emerson Climate Technologies, Inc. Module de capteur pour compresseur
WO2009112479A1 (fr) * 2008-03-10 2009-09-17 Burckhardt Compression Ag Procédé et dispositif de production de combustible gaz naturel

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007052899A1 (de) * 2007-11-07 2009-05-14 Ford Global Technologies, LLC, Dearborn Aufgeladene Brennkraftmaschine und Verfahren zum Betreiben einer derartigen Brennkraftmaschine
DE102011084666A1 (de) * 2011-02-11 2012-08-16 Continental Teves Ag & Co. Ohg Kompressorschaltung für eine pneumatische Regelvorrichtung eines Fahrzeugs
US20130280095A1 (en) * 2012-04-20 2013-10-24 General Electric Company Method and system for reciprocating compressor starting
DE102014012646B4 (de) * 2014-08-22 2023-06-07 Zf Cv Systems Hannover Gmbh Druckluftversorgungsanlage, pneumatisches System und Verfahren zum Steuern einer Druckluftversorgungsanlage

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4236876A (en) * 1979-07-30 1980-12-02 Carrier Corporation Multiple compressor system
US5797729A (en) * 1996-02-16 1998-08-25 Aspen Systems, Inc. Controlling multiple variable speed compressors
WO2009058356A1 (fr) * 2007-11-02 2009-05-07 Emerson Climate Technologies, Inc. Module de capteur pour compresseur
WO2009112479A1 (fr) * 2008-03-10 2009-09-17 Burckhardt Compression Ag Procédé et dispositif de production de combustible gaz naturel

Also Published As

Publication number Publication date
EP3311028B1 (fr) 2019-06-05
US20180180039A1 (en) 2018-06-28
EP3311028A1 (fr) 2018-04-25
DE102015007731A1 (de) 2016-12-22

Similar Documents

Publication Publication Date Title
EP3601797B1 (fr) Compresseur à piston avec une zone de reglage étendu
DE202015004596U1 (de) Vakuumpumpensystem
WO2012013530A1 (fr) Procédé pour faire fonctionner un compresseur
WO2006063947A1 (fr) Procede de fonctionnement d'un compresseur alimente par convertisseur
DE102012105951A1 (de) Pumpensystem zur Evakuierung von Gas aus einer Mehrzahl von Kammern sowie Verfahren zur Steuerung des Pumpensystems
EP2821650A2 (fr) Pompe sous vide à membrane
EP3311028B1 (fr) Procédé pour comprimer un gaz, unité de calcul et compresseur à piston polyétagé
WO2014001090A1 (fr) Procédé et ensemble pompe permettant de faire le vide dans une chambre
EP3183446B1 (fr) Unité de compresseur et son procédé de fonctionnement
EP3388677A1 (fr) Procédé de commande d'un compresseur à vis
EP3071837A1 (fr) Système de pompe à vide et procédé pour faire fonctionner un système de pompe à vide
DE10255792A1 (de) Verfahren zur Steuerung einer Vakuumpumpe sowie Vakuumpumpensystem
EP2357115B2 (fr) Compresseur à air comprimé et procédé de fonctionnement d'un compresseur à air comprimé
WO2015139855A1 (fr) Dispositif pour obturer et gonfler des objets gonflables
EP3619066A1 (fr) Ensemble d'étranglement ainsi que système de régulation de la pression comprenant un ensemble d'étranglement de ce type
EP3983681B1 (fr) Procédé de détection des dommages sur un compresseur
DE202014007963U1 (de) Vakuumpumpsystem
EP3548745A1 (fr) Procédé permettant de faire fonctionner un système de pompage à vide
DE202011103269U1 (de) Druckluftversorgungsanlage
WO2021097505A1 (fr) Compresseur
EP3619062B1 (fr) Procédé permettant de faire fonctionner un système de régulation de la pression dans un véhicule ainsi que système de régulation de la pression
DE102018102397A1 (de) Steuerventilanordnung zur indirekten pneumatischen Steuerung
DE102014111946A1 (de) Verfahren zum Betreiben einer Kälteanlage
DE102010055058A1 (de) Verfahren zum Belüften einer Vakuumpumpe und Anordnung mit einer Vakuumpumpe
DE102015111287A1 (de) Kompressor und Verfahren zu dessen Drehzahlsteuerung

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: 16728839

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 15580433

Country of ref document: US

NENP Non-entry into the national phase

Ref country code: DE