EP0757179B1 - Kompressionsvorrichtung - Google Patents

Kompressionsvorrichtung Download PDF

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Publication number
EP0757179B1
EP0757179B1 EP95810491A EP95810491A EP0757179B1 EP 0757179 B1 EP0757179 B1 EP 0757179B1 EP 95810491 A EP95810491 A EP 95810491A EP 95810491 A EP95810491 A EP 95810491A EP 0757179 B1 EP0757179 B1 EP 0757179B1
Authority
EP
European Patent Office
Prior art keywords
compression
accordance
compression apparatus
compressor
stages
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.)
Expired - Lifetime
Application number
EP95810491A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0757179A1 (de
Inventor
Walter Aicher
Heinrich Lorenzen
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.)
MAN Turbo AG
Original Assignee
MAN Turbomaschinen AG GHH Borsig
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 MAN Turbomaschinen AG GHH Borsig filed Critical MAN Turbomaschinen AG GHH Borsig
Priority to EP95810491A priority Critical patent/EP0757179B1/de
Priority to DE59510130T priority patent/DE59510130D1/de
Priority to JP8191983A priority patent/JPH09119394A/ja
Priority to US08/688,598 priority patent/US5791159A/en
Priority to NO963184A priority patent/NO308555B1/no
Publication of EP0757179A1 publication Critical patent/EP0757179A1/de
Application granted granted Critical
Publication of EP0757179B1 publication Critical patent/EP0757179B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage pumps
    • F04D17/14—Multi-stage pumps with means for changing the flow-path through the stages, e.g. series-parallel, e.g. side-loads
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
    • F04D29/5826—Cooling at least part of the working fluid in a heat exchanger
    • F04D29/5833—Cooling at least part of the working fluid in a heat exchanger flow schemes and regulation thereto
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
    • F04D29/5846—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps cooling by injection
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/0002—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the fluid to be liquefied
    • F25J1/0022—Hydrocarbons, e.g. natural gas
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/006—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the refrigerant fluid used
    • F25J1/008—Hydrocarbons
    • F25J1/0087—Propane; Propylene
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
    • F25J1/0243—Start-up or control of the process; Details of the apparatus used; Details of the refrigerant compression system used
    • F25J1/0279—Compression of refrigerant or internal recycle fluid, e.g. kind of compressor, accumulator, suction drum etc.
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
    • F25J1/0243—Start-up or control of the process; Details of the apparatus used; Details of the refrigerant compression system used
    • F25J1/0279—Compression of refrigerant or internal recycle fluid, e.g. kind of compressor, accumulator, suction drum etc.
    • F25J1/0294—Multiple compressor casings/strings in parallel, e.g. split arrangement

Definitions

  • the invention relates to a compression device comprising a turbo compressor according to the preamble of claim 1.
  • the first pre-cooling stage is often a propane circuit is used, which with a large Turbo compressor is operated.
  • the propane circuit is usually designed with several cooling stages, whereby a multi-stage compressor with one or more Intermediate feeds are used.
  • Such one Cooling system with propane circuit and intermediate feeds is known from "Refrigeration System Stability Linked to Compressor and Process Characteristics, Clifford.E. Lucas, Chemical Engineering Process, November 1989 ", the intermediate feed known therefrom in FIG. 1 is shown.
  • a disadvantage of this known cooling device is therein to see them under certain operating conditions tends to be unstable.
  • a reason for that is can be seen in the intermediate feed, their feed quantity can be very large, sometimes larger than the respective one Main stream in the compression stage.
  • the feed amount has a lower temperature than the main stream.
  • the Mixture of main flow and feed quantity can be Entry into the impeller an inhomogeneous mixing ratio have what results in a compression stage unstable behavior.
  • Another disadvantage of the known cooling device is in seeing that they are a relatively thick wave required because a plurality of impellers on the shaft are arranged.
  • the task is solved in particular by the fact that a mixing device outside the turbo compressor is arranged that in relation to the current direction of the Main stream previous and one of these following Compression levels via the mixing device with each other are connected, and that for the following Compression level provided feed current in the Mixing device opens to the feed stream with a Outlet stream or main stream of the previous one Mix compression level.
  • An advantage of the invention is that the Mixing device a good mixing of main stream and feed current causes, so that in the next Compression level a fluid with a homogeneous Temperature distribution is fed. this leads to a more stable operating behavior of the compression level.
  • a propane cooling circuit can be a volume of Have intermediate feeds, some of which is greater than that of the main stream and also one has lower temperature. By mixing this two volume flows outside the compressor achieved that the machine characteristics completely regardless of the admixed volume and its Temperature can be determined precisely.
  • a Thermodynamic design of a compressor can thus in a completely conventional way due to the averaged Entry state of the fluid can be performed.
  • Another advantage of the invention is that that the compression device into several, individual Compressors can be divided. It is particularly advantageous the use of compressors with two against each other arranged impellers. This can prevent the entry of the Fluids can be arranged in the compressor at the free end. This allows the diameter of the shaft and thus the Mach number at the entry of the impeller can be kept low. As a result, the characteristic of the compression level stable over a wide range. This allows for given speed and necessary impeller diameter smaller diameter of the impeller cover plate and thus achieve a lower entry Mach number.
  • Fig. 1 shows a known from the prior art Compressor 1 arranged on a shaft 2 Impellers 11a, 11b which are used to compress a Serve coolant.
  • the compressor 1 will A feed stream 5b via an inlet opening 1f supplied, which within the compressor housing 1e in the one already compressed by the impeller 11a Main stream 6a open.
  • 1e in the compressor housing correspondingly shaped internal channels 60a, 60b, 61a arranged.
  • the two streams 6a, 5b are mixed and from the subsequent impeller 11b to a main stream 6b further compressed.
  • a disadvantage of this arrangement is to see that the two streams 6a, 5b are not mix homogeneously, resulting in unstable behavior the flow in the impeller 11b can lead.
  • Fig. 3 shows a schematic representation of a known, multi-stage coolant circuit with propane, as for large refrigeration circuits in LPG systems or LNG plants are used.
  • the compressor has 4 in Series connected and on a common shaft 2 arranged compression stages 1a, 1b, 1c, 1d.
  • the compressed coolant arrives via the final flow 6d a capacitor 3 and then on to process 4.
  • the only schematically illustrated process 4 leads the individual compression stages 1a, 1b, 1c, 1d feed streams 5b, 5c, 5d too.
  • Fig. 2a shows a schematic representation of a Embodiment of the invention Compression device. This points to a common shaft 2 arranged in series Compression levels 1a, 1b, 1c, 1d.
  • the final current 6d or the final withdrawal in turn leads to a compressor 3 in the process not shown in detail 4.
  • From the Process 4 is the coolant through the base stream 5a and the feed currents 5b, 5c, 5d to the individual Compression stages 1a, 1b, 1c, 1d fed again.
  • there are the individual compression stages 1a, 1b, 1c, 1d configured that the coolant via a Extraction line 6a, 6b, 6c through which the main flow flows out of the compressor housing 1e again is directed.
  • Mixing devices 8a, 8b, 8c are outside the compressor housing 1e Mixing devices 8a, 8b, 8c arranged, in which both the feed stream 5b, 5c, 5d as well as the main stream 6a, 6b, 6c, and after mixing of these two streams via the feed line 7a, 7b, 7c Compression stages 1b, 1c, 1d is fed back.
  • the Both streams 5b, 6a are in the mixing device 8a mixed so that the stream with a homogeneous Temperature distribution and a homogeneous Speed distribution from the mixing device 8a emerges and is supplied to the compression stage 1b.
  • Mixer device is suitable for a variety of Embodiments, especially a static one Mixer, which is known only inside statically arranged, the fluid homogenizing Features internals.
  • An advantage of the invention is that the compression levels 1a, 1b, 1c, 1d to different Arrange kind on a common shaft 2, or arrange themselves on several, separate waves 2 to let. 2b shows a schematically represented Embodiment, which, compared to Fig. 2a, by a different arrangement of the Compression stages 1a, 1b, 1c, 1d on shaft 2 distinguished.
  • Arranged adjacent on the shaft 2 Compression levels 1a, 1b, 1c, 1d are against each other arranged, i.e. the fluid is arranged adjacent Compression stages 1a, 1b, 1c, 1d flow axially in opposite direction. That's how they are Compression stages 1a and 1b, or 1b and 1c, or 1c and 1d arranged against each other.
  • Fig. 4 shows that shown in Fig. 2b Embodiment in a more detailed Design.
  • the shaft 2 shown in Fig. 2b is in 4 divided into two separate shafts 2, which are connected via a connecting shaft 2a are interconnected.
  • the compression device 10 comprises two compressors 1, which via the Connection shaft 2a are connected to each other, as well as the Mixing devices 8a, 8b, 8c and the fluid streams conducting Connection lines 5a, 5b, 5c, 5d, 6a, 6b, 6c, 6d.
  • everyone Compressor 1 has two compression stages 1a, 1b, 1c, 1d on, as shown in FIG. 5, on the shaft 2 are arranged against each other.
  • a drive device 12 for example an electric motor, a gas turbine or a steam turbine, drives the first shaft 2, whereby this via the connecting shaft 2a with the shaft 2 of the second compressor 1 directly or via a transmission connected and drives it.
  • One and Outlet openings of compression stages 1a, 1b, 1c, 1d are led outside so that outside the compressors 1 the mixing devices 8a, 8b, 8c can be arranged and could be connected with pipes accordingly the base current 5a, the feed currents 5b, 5c, 5d and the Main streams 6a, 6b, 6c and the final stream 6d accordingly conduct.
  • Fig. 5 shows the upper part of a longitudinal section through a compressor 1 as used in FIG. 4.
  • the Compressor housing 1e has correspondingly shaped channels on, so that the refrigerant flow 7a, 7b into the compressor 1 occurs, through which impellers 11a, 11b are compressed, and again as a removal flow or main flow 6b, 6c the compressor 1 exits.
  • Such is the one shown Compressor two compression stages 1b, 1c.
  • the shaft 2 and thus the Entry diameter of the impeller is relatively small be designed.
  • the arrangement according to FIG. 5 allows a relatively thin shaft 2 and impellers 11a, 11b to use a small diameter.
  • Impellers 11a, 11b have a smaller Mach number, which a higher flow stability of the fluid in the compressor 1, in particular in the impeller 11a, 11b.
  • Fig. 6 shows a further embodiment of a Compressor 1, which on the right side Compression stage 1a with a compressor stage, and on the left side a compression level 1b two compressor stages 1e, 1f connected in series, so that the refrigerant flow 5a only in the main flow 6a again exit.
  • a compressor stage 1e, 1f one Compaction level understood, which is a single impeller for compression.
  • a compression stage 1a, 1b can have a single compressor stage 1e, 1f, or also a plurality of series Compressor stages 1e, 1f.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP95810491A 1995-07-31 1995-07-31 Kompressionsvorrichtung Expired - Lifetime EP0757179B1 (de)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP95810491A EP0757179B1 (de) 1995-07-31 1995-07-31 Kompressionsvorrichtung
DE59510130T DE59510130D1 (de) 1995-07-31 1995-07-31 Kompressionsvorrichtung
JP8191983A JPH09119394A (ja) 1995-07-31 1996-07-22 圧縮装置
US08/688,598 US5791159A (en) 1995-07-31 1996-07-30 Compression apparatus
NO963184A NO308555B1 (no) 1995-07-31 1996-07-30 Kompressoranordning

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP95810491A EP0757179B1 (de) 1995-07-31 1995-07-31 Kompressionsvorrichtung

Publications (2)

Publication Number Publication Date
EP0757179A1 EP0757179A1 (de) 1997-02-05
EP0757179B1 true EP0757179B1 (de) 2002-03-27

Family

ID=8221779

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95810491A Expired - Lifetime EP0757179B1 (de) 1995-07-31 1995-07-31 Kompressionsvorrichtung

Country Status (5)

Country Link
US (1) US5791159A (no)
EP (1) EP0757179B1 (no)
JP (1) JPH09119394A (no)
DE (1) DE59510130D1 (no)
NO (1) NO308555B1 (no)

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TW480325B (en) * 1999-12-01 2002-03-21 Shell Int Research Plant for liquefying natural gas
MY125082A (en) * 1999-12-15 2006-07-31 Shell Int Research Compression apparatus for gaseous refrigerant
BE1013692A3 (nl) * 2000-09-19 2002-06-04 Atlas Copco Airpower Nv Hogedruk, meertraps-centrifugaalcompressor.
DE50312744D1 (de) * 2002-06-04 2010-07-08 Alstom Technology Ltd Verfahren zum betreiben eines verdichters
DE10251486A1 (de) * 2002-11-05 2004-05-19 Linde Ag Verfahren und Vorrichtung zur Gaserückgewinnung
US6962060B2 (en) * 2003-12-10 2005-11-08 Air Products And Chemicals, Inc. Refrigeration compression system with multiple inlet streams
JP2009519429A (ja) * 2005-12-16 2009-05-14 シエル・インターナシヨネイル・リサーチ・マーチヤツピイ・ベー・ウイ 冷媒回路
US20070204649A1 (en) * 2006-03-06 2007-09-06 Sander Kaart Refrigerant circuit
ATE506542T1 (de) * 2006-03-24 2011-05-15 Siemens Ag Verdichtereinheit
RU2499962C2 (ru) * 2007-12-04 2013-11-27 Шелл Интернэшнл Рисерч Маатсхаппий Б.В. Способ и устройство для охлаждения и/или ожижения углеводородного потока
ITAN20070063A1 (it) * 2007-12-04 2009-06-05 S Tra Te G I E S R L Impianto ad alta efficienza energetica per compressione di metano per autotrazione
JP4990112B2 (ja) 2007-12-05 2012-08-01 株式会社日立製作所 冷凍サイクルシステム、天然ガス液化設備、ヒートポンプシステム、及び冷凍サイクルシステムの改造方法
JP4974875B2 (ja) * 2007-12-28 2012-07-11 トヨタ自動車株式会社 圧縮機の固定構造体
US8544256B2 (en) * 2008-06-20 2013-10-01 Rolls-Royce Corporation Gas turbine engine and integrated heat exchange system
US20100147024A1 (en) * 2008-12-12 2010-06-17 Air Products And Chemicals, Inc. Alternative pre-cooling arrangement
IT1392796B1 (it) 2009-01-23 2012-03-23 Nuovo Pignone Spa Sistema reversibile di iniezione ed estrazione del gas per macchine rotative a fluido
FI122720B (fi) * 2010-07-13 2012-06-15 Tamturbo Oy Turbokompressorin säätöratkaisu
ITFI20130076A1 (it) * 2013-04-04 2014-10-05 Nuovo Pignone Srl "integrally-geared compressors for precooling in lng applications"
ITUB20152497A1 (it) 2015-07-24 2017-01-24 Nuovo Pignone Tecnologie Srl Treno di compressione di gas di carica di etilene
JP6653157B2 (ja) * 2015-10-30 2020-02-26 三菱重工サーマルシステムズ株式会社 遠心圧縮機械の戻り流路形成部、遠心圧縮機械
ITUA20164168A1 (it) * 2016-06-07 2017-12-07 Nuovo Pignone Tecnologie Srl Treno di compressione con due compressori centrifughi e impianto lng con due compressori centrifughi
IT201600080745A1 (it) * 2016-08-01 2018-02-01 Nuovo Pignone Tecnologie Srl Compressore di refrigerante diviso per la liquefazione di gas naturale
JP7085306B2 (ja) * 2017-02-20 2022-06-16 三菱重工コンプレッサ株式会社 遠心圧縮機

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Also Published As

Publication number Publication date
JPH09119394A (ja) 1997-05-06
EP0757179A1 (de) 1997-02-05
NO963184D0 (no) 1996-07-30
NO308555B1 (no) 2000-09-25
US5791159A (en) 1998-08-11
DE59510130D1 (de) 2002-05-02
NO963184L (no) 1997-02-03

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