US20180180039A1 - Method for compressing a gas, computing unit and multi-stage piston compressor - Google Patents

Method for compressing a gas, computing unit and multi-stage piston compressor Download PDF

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Publication number
US20180180039A1
US20180180039A1 US15/580,433 US201615580433A US2018180039A1 US 20180180039 A1 US20180180039 A1 US 20180180039A1 US 201615580433 A US201615580433 A US 201615580433A US 2018180039 A1 US2018180039 A1 US 2018180039A1
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US
United States
Prior art keywords
compression stage
stage
gas
compression
valve
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Abandoned
Application number
US15/580,433
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English (en)
Inventor
Robert Adler
Sascha Dorner
Markus Stephan
Christoph Nagl
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Linde GmbH
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Linde GmbH
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Filing date
Publication date
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Assigned to LINDE AKTIENGESELLSCHAFT reassignment LINDE AKTIENGESELLSCHAFT ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: DORNER, SASCHA, ADLER, ROBERT, Nagl, Christoph, STEPHAN, MARKUS
Publication of US20180180039A1 publication Critical patent/US20180180039A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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
    • 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
    • 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 pertains to a method for compressing a gas by means of a multi-stage piston compressor, a computing unit for carrying out said method, as well as such a multi-stage piston compressor.
  • Devices for compressing gases are generally known.
  • reciprocating piston compressors, rotary compressors or ionic compressors can be used for this purpose.
  • Higher compression ratios can be achieved, for example, by using a multi-stage configuration of compression devices. In this case, individual stages usually separated from one another by valves or gate valve gears.
  • such compression devices or compressors are typically designed for defined parameters such as pressures, piston diameters and therefore also gas forces. It is therefore frequently difficult to realize a change of these parameters on existing systems.
  • compressors with drives in the form of linear motors may be designed such that the compressive force of the individual compression stages is higher than the attainable maximum power of the linear motor.
  • An operational superposition of the oscillating mass force and the compressive forces results in a maximum force that has to be lower than the maximum attainable power of the linear motor. In this way, high pressures can also be generated by small driving mechanisms without having to use small piston diameters and thereby forfeiting capacity.
  • the inventive method serves for compressing a gas by means of a multi-stage piston compressor. If an inlet pressure of the first compression stage exceeds a threshold value, the gas is at least partially, in particular completely, diverted upstream of the first compression stage and fed to a second compression stage, which directly follows the first compression stage.
  • the stroke of a piston of the piston compressor which is assigned to the first compression stage, is advantageously reduced.
  • An excessively low cylinder pressure in the first compression stage can thereby also be prevented (the compression device ejects gas through an outlet valve while the inlet valve is closed, but no additional gas inflow can take place and the remaining gas is expanded such that a pressure drop occurs in the cylinder), wherein such an excessively low cylinder pressure could lead, e.g., to a shutdown because air would otherwise be drawn in from outside and mix with the gas to be compressed.
  • the power consumption of the compressor can thereby also be reduced.
  • the stroke is advantageously reduced in dependence on a residual pressure after a reexpansion in the first compression stage and/or an inlet pressure of the second compression stage.
  • the higher the residual pressure after a reexpansion in the first compression stage and/or the higher the inlet pressure of the second compression stage (referred to the stroke reduction), the smaller the amount, by which the stroke is reduced.
  • the clearance volume of the respective cylinder of the first compression stage may particularly also be taken into consideration, in this way, the operation of the compressor can be optimally adapted to the respective circumstances.
  • the reduction of the stroke is determined based on stored the values for the residual pressure and/or the inlet pressure of the second compression stage.
  • the values for the stroke reduction may be stored, e.g. in a control unit for the compressor, in increments corresponding to 0.5 bar of the respective pressures.
  • the gas is advantageously diverted upstream of the first compression stage and fed to the second compression stage in that a first valve in a first flow path leading to the first compression stage is at least partially closed and a second valve in a second flow path leading from the first flow path to the second compression stage is at least partially opened.
  • a first valve in a first flow path leading to the first compression stage is at least partially closed
  • a second valve in a second flow path leading from the first flow path to the second compression stage is at least partially opened.
  • An inlet valve of the first compression stage is advantageously used as first valve.
  • the inlet valve is simply shut in order to be closed. In this way, no additional valve other than the second valve is required in the second flow path.
  • An inventive computing unit is designed for carrying out the inventive method.
  • a computing unit may be realized, e.g., in the form of a stored program control (SPC).
  • the computing unit is particularly designed for acquiring and processing the required parameters and for correspondingly activating the required components.
  • An inventive multi-stage reciprocating piston compressor comprises a gas inlet, a first compression stage and a second compression stage.
  • a first valve is arranged in a first flow path leading to a gas inlet of the first compression stage and a second flow path branches off the first flow path upstream of the first valve and leads to a gas inlet of the second compression stage.
  • a second valve is arranged in the second flow path.
  • the first valve is preferably formed by the inlet valve of the first compression stage.
  • the multi-stage reciprocating piston compressor advantageously comprises at least one electric linear motor for moving pistons of the reciprocating piston compressor.
  • the multi-stage reciprocating piston compressor comprises an inventive computing unit.
  • the piston compressor is used for compressing gases.
  • the piston compressor is particularly used for compressing carbon dioxide, hydrogen, methane, natural gas, helium or nitrogen.
  • the reciprocating compressor for compressing gas is preferably operated at temperatures between ⁇ 253 and 150° C.
  • the piston compressor preferably can compress the gas to pressures between 0.1 bar and 1000 bar.
  • the temperatures and pressures are dependent on the gas to be compressed.
  • gases may also consist of wet and/or contaminated gases or of gas mixtures.
  • the inlet temperature of the carbon dioxide preferably lies between ⁇ 60° C. and 120° C., particularly between 1 and 80° C.
  • the outlet temperature of the carbon dioxide preferably lies between 40 and 150° C., particularly between 60 and 100° C.
  • the inlet pressure of the carbon dioxide preferably lies between 0.1 bar and 10 bar, particularly between 0.2 and 4 bar.
  • the outlet pressure of the carbon dioxide preferably lies between 5 and 100 bar, particularly between 20 and 60 bar.
  • the volumetric flow rate preferably lies between 0.5 Nm 3 /h and 50 Nm 3 /h, particularly between 1 Nm 3 /h and 8 Nm 3 /h.
  • the inlet temperature of the hydrogen (temperature prior to the compression) preferably lies between ⁇ 253° C. and 80° C., particularly between ⁇ 253° C. and ⁇ 80° C. when the compressor is used in the form of a cryogenic compressor or particularly between ⁇ 20° C. and 80° C. when the compressor is used in the form of an ionic compressor.
  • the outlet temperature of the hydrogen. (temperature after the compression) preferably lies between ⁇ 250 and 150° C., particularly between ⁇ 60 and 80° C.
  • the inlet pressure of the hydrogen (pressure prior to the compression) preferably lies between 0.8 bar and 40 bar, particularly between 2.5 and 30 bar.
  • the outlet pressure of the hydrogen (pressure after the compression) preferably lies between 10 and 1000 bar, particularly between 500 and 1000 bar.
  • the volumetric flow rate preferably lies between 0.5 Nm 3 /h and 500 Nm 3 /h, particularly between 50 Nm 3 /h and 350 Nm 3 /h.
  • the inlet temperature of the methane or natural gas (temperature prior to the compression) preferably lies between ⁇ 182° C. and 80° C., particularly between ⁇ 182° C. and ⁇ 40° C. when the compressor is used in the form of a cryogenic compressor or particularly between ⁇ 20° C. and 80° C. when the compressor is used in the form of an ionic compressor.
  • the outlet temperature of the methane or natural gas (temperature after the compression) preferably lies between ⁇ 180 and 150° C., particularly between ⁇ 60 and 80° C.
  • the inlet pressure of the methane or natural gas (pressure prior to the compression) preferably lies between 0.8 bar and 30 bar, particularly between 1.5 and 20 bar.
  • the outlet pressure of the methane or natural gas preferably lies between 10 and 650 bar, particularly between 300 and 600 bar.
  • the volumetric flow rate preferably lies between 0.5 Nm 3 /h and 1000 Nm 3 /h, particularly between 5 Nm 3 /h and 350 Nm 3 /h.
  • the inlet temperature of the helium (temperature prior to the compression) preferably lies between ⁇ 269° C. and 80° C., particularly between ⁇ 269° C. and ⁇ 80° C. when the compressor is used in the form of a cryogenic compressor or particularly between ⁇ 20° C. and 80° C. when the compressor is used in the form of an ionic compressor.
  • the outlet temperature of the helium (temperature after the compression) preferably lies between ⁇ 269 and 150° C., particularly between ⁇ 60 and 80° C.
  • the inlet pressure of the helium (pressure prior to the compression) preferably lies between 0.8 bar and 40 bar, particularly between 2.5 and 20 bar.
  • the outlet pressure of the helium (pressure after the compression) preferably lies between 10 and 1000 bar, particularly between 200 and 600 bar.
  • the volumetric flow rate preferably lies between 0.5 Nm 3 /h and 600 Nm 3 /h, particularly between 50 Nm 3 /h and 400 Nm 3 /h.
  • the inlet temperature of the nitrogen (temperature prior to the compression) preferably lies between ⁇ 196° C. and 80° C., particularly between ⁇ 196° C. and ⁇ 40° C. when the compressor is used in the form of a cryogenic compressor or particularly between ⁇ 20° C. and 80° C. when the compressor is used in the form of an ionic compressor.
  • the outlet temperature of the nitrogen. (temperature after the compression) preferably lies between ⁇ 195 and 150° C., particularly between ⁇ 60 and 80° C.
  • the inlet pressure of the nitrogen (pressure prior to the compression) preferably lies between 0.8 bar and 30 bar, particularly between 1.5 and 17 bar.
  • the outlet pressure of the nitrogen (pressure after the compression) preferably lies between 10 and 650 bar, particularly between 200 and 400 bar.
  • the volumetric flow rate preferably lies between 0.5 Nm 3 /h and 500 Nm 3 /h, particularly between 5 Nmj/h and 350 Nm 3 /h.
  • FIG. 1 schematically shows an inventive multi-stage reciprocating compressor according to a preferred embodiment in the form of a flowchart.
  • FIG. 2 schematically shows stroke profiles of an inventive multi-stage reciprocating compressor according to a preferred embodiment in the form of a diagram.
  • FIG. 1 schematically shows an inventive multi-stage piston compressor 100 according to a preferred embodiment in the form of a flowchart.
  • the piston compressor 100 comprises a first compression stage 110 and a second compression stage 120 . Both compression stages are respectively realized in the form of pistons that move in a cylinder. These pistons are driven by an electric linear motor 130 . Additional compression stages may naturally be provided.
  • the first compression stage comprises an inlet valve ill and an outlet valve 112 , which may be realized in the form of pressure-controlled check valves.
  • the second compression stage 120 likewise comprises an inlet valve 121 and an outlet valve 122 , which may also be realized in the form of pressure-controlled check valves.
  • the regular gas flow takes place along a first flow path 161 (illustrated on the left in FIG. 1 ) leading to the first compression stage 110 and then from the first compression stage 110 to the second compression stage 120 . Subsequently, the gas can be fed to a desired application.
  • Pressure sensors 141 , 142 and 143 are furthermore provided. An inlet pressure of the first compression stage can be measured with the pressure sensor 141 , an outlet pressure of the first compression stage 110 or an inlet pressure of the second compression stage 120 can be respectively measured with the pressure sensor 142 and an outlet pressure of the second compression stage 120 can be measured with the pressure sensor 143 .
  • the pressure sensors 141 , 142 and 143 are connected to a computing unit 170 , which is realized in the form of a stored program control (SPC).
  • the SPC 170 can therefore respectively acquire or read out the corresponding pressures.
  • a first valve 151 is furthermore provided in the first flow path 161 .
  • This first valve 151 can presently be activated, i.e. opened and closed, by means of the SPC 170 .
  • the first valve 151 is open during the normal operation.
  • a second flow path 162 in the sense of a bypass line is furthermore provided, wherein this second flow path branches off the first flow path 161 , namely upstream of the first valve 151 , and leads to the second compression stage 120 .
  • a second valve 152 which can likewise be activated, i.e. opened and closed, by the SPC 170 , is provided in the second flow path 162 . This second valve 152 is closed during the normal operation.
  • the first valve 151 is completely closed if the SPC 170 respectively acquires or reads out an inlet pressure of the first compression stage 110 , which lies above a threshold value, from the pressure sensor 141 during the operation of the piston compressor 100 .
  • the second valve 152 simultaneously is completely opened. The gas now flows directly to the inlet of the second compression stage 120 instead of to the first compression stage 110 .
  • This threshold value can preferably be chosen in such a way that the output or the attainable power of the electric linear motor 130 for the first compression stage 110 just barely suffices for carrying out the required compression at inlet pressures below this threshold value. Inlet pressures, at which the required compression can no longer be carried out, are thereby prevented in the first compression stage 110 .
  • the electric linear motor 130 is furthermore activated by the SPC 170 in such a way that the stroke of the piston assigned to the first compression stage 110 is reduced.
  • FIG. 2 schematically shows stroke profiles of an inventive multi-stage reciprocating piston compressor according to a preferred embodiment in the form of a diagram.
  • the stroke h is plotted as a function of the time t.
  • h 1 denotes the stroke profile of the piston assigned to the first compression stage and h 2 denotes the stroke profile of the piston assigned to the second compression stage.
  • the stroke h 1 of the piston of the first compression stage is now reduced by an amount ⁇ h such that the piston of the first compression stage now has a stroke h′ 1 .
  • the stroke of the piston of the second compression stage remains unchanded. As initially mentioned, a negative pressure in the second compression stage is thereby prevented.
  • the amount ⁇ h, by which the stroke is reduced can be calculated based on the following formula:
  • p1 denotes the residual pressure after the reexpansion in the first compression stage.
  • the pressure p1 may be a freely definable pressure that should preclude an absolute pressure from falling short of 1 bar. In this context, p1>>1 bar absolute should preferably apply.
  • the pressure after the reexpansion may be determined computationally or ascertained indirectly if the pressure p1 drops below the pressure measured by the pressure sensor 141 in the reexpansion period. In this case, gas from the volume between the valves 151 , 111 and the pressure sensor 141 would flow in such that the pressure measured by the pressure sensor 141 would drop.
  • the reference symbol p2 denotes the inlet pressure of the second compression stage, which is measured by the pressure sensor 142 .
  • the reference symbol ⁇ denotes the ratio of specific heats of the adiabatic change and the reference symbol V stat denotes a static clearance volume of the first compression stage, which results from the dimensions of the piston and the cylinder.
  • the reference symbol d ultimately denotes the diameter of the piston of the first compression stage. In other words, the clearance volume of the first compression stage is increased due to the stroke reduction.

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  • 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)
US15/580,433 2015-06-16 2016-06-11 Method for compressing a gas, computing unit and multi-stage piston compressor Abandoned US20180180039A1 (en)

Applications Claiming Priority (3)

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
PCT/EP2016/000973 WO2016202443A1 (de) 2015-06-16 2016-06-11 Verfahren zum verdichten eines gases, recheneinheit und mehrstufiger kolbenverdichter

Publications (1)

Publication Number Publication Date
US20180180039A1 true US20180180039A1 (en) 2018-06-28

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US15/580,433 Abandoned US20180180039A1 (en) 2015-06-16 2016-06-11 Method for compressing a gas, computing unit and multi-stage piston compressor

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US (1) US20180180039A1 (de)
EP (1) EP3311028B1 (de)
DE (1) DE102015007731A1 (de)
WO (1) WO2016202443A1 (de)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
CN113533600A (zh) * 2021-08-09 2021-10-22 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、装置、检测方法及装置

Families Citing this family (1)

* 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

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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
US8160827B2 (en) * 2007-11-02 2012-04-17 Emerson Climate Technologies, Inc. Compressor sensor module
DE102007052899A1 (de) * 2007-11-07 2009-05-14 Ford Global Technologies, LLC, Dearborn Aufgeladene Brennkraftmaschine und Verfahren zum Betreiben einer derartigen Brennkraftmaschine
EP2296962B1 (de) * 2008-03-10 2011-11-16 Burckhardt Compression AG Vorrichtung und verfahren zum bereitstellen von erdgasbrennstoff
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

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113533600A (zh) * 2021-08-09 2021-10-22 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、装置、检测方法及装置

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WO2016202443A1 (de) 2016-12-22
EP3311028B1 (de) 2019-06-05
EP3311028A1 (de) 2018-04-25
DE102015007731A1 (de) 2016-12-22

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