EP2604862A1 - Kompressoranordnung - Google Patents

Kompressoranordnung Download PDF

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Publication number
EP2604862A1
EP2604862A1 EP11193001.2A EP11193001A EP2604862A1 EP 2604862 A1 EP2604862 A1 EP 2604862A1 EP 11193001 A EP11193001 A EP 11193001A EP 2604862 A1 EP2604862 A1 EP 2604862A1
Authority
EP
European Patent Office
Prior art keywords
stage
compressor
air
drive shaft
driven
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.)
Withdrawn
Application number
EP11193001.2A
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English (en)
French (fr)
Inventor
Nicolas John Haryett
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.)
Air Products and Chemicals Inc
Original Assignee
Air Products and Chemicals Inc
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 Air Products and Chemicals Inc filed Critical Air Products and Chemicals Inc
Priority to EP11193001.2A priority Critical patent/EP2604862A1/de
Priority to TW101146156A priority patent/TW201331463A/zh
Priority to PCT/EP2012/075044 priority patent/WO2013087606A1/en
Priority to CN2012206828394U priority patent/CN203201825U/zh
Publication of EP2604862A1 publication Critical patent/EP2604862A1/de
Withdrawn legal-status Critical Current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
    • 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
    • F04D25/16—Combinations of two or more pumps ; Producing two or more separate gas flows
    • F04D25/163—Combinations of two or more pumps ; Producing two or more separate gas flows driven by a common gearing arrangement
    • 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
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • F25J3/02—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream
    • F25J3/04—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air
    • F25J3/04006—Providing pressurised feed air or process streams within or from the air fractionation unit
    • F25J3/04012—Providing pressurised feed air or process streams within or from the air fractionation unit by compression of warm gaseous streams; details of intake or interstage cooling
    • F25J3/04018—Providing pressurised feed air or process streams within or from the air fractionation unit by compression of warm gaseous streams; details of intake or interstage cooling of main feed air
    • 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
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • F25J3/02—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream
    • F25J3/04—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air
    • F25J3/04006—Providing pressurised feed air or process streams within or from the air fractionation unit
    • F25J3/04012—Providing pressurised feed air or process streams within or from the air fractionation unit by compression of warm gaseous streams; details of intake or interstage cooling
    • F25J3/04024—Providing pressurised feed air or process streams within or from the air fractionation unit by compression of warm gaseous streams; details of intake or interstage cooling of purified feed air, so-called boosted air
    • 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
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • F25J3/02—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream
    • F25J3/04—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air
    • F25J3/04006—Providing pressurised feed air or process streams within or from the air fractionation unit
    • F25J3/04109—Arrangements of compressors and /or their drivers
    • F25J3/04115—Arrangements of compressors and /or their drivers characterised by the type of prime driver, e.g. hot gas expander
    • F25J3/04121—Steam turbine as the prime mechanical driver
    • 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
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • F25J3/02—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream
    • F25J3/04—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air
    • F25J3/04006—Providing pressurised feed air or process streams within or from the air fractionation unit
    • F25J3/04109—Arrangements of compressors and /or their drivers
    • F25J3/04145—Mechanically coupling of different compressors of the air fractionation process to the same driver(s)
    • 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
    • F25J2230/00—Processes or apparatus involving steps for increasing the pressure of gaseous process streams
    • F25J2230/20—Integrated compressor and process expander; Gear box arrangement; Multiple compressors on a common shaft

Definitions

  • the present invention relates to a compressor arrangement suitable for use where high air flow rates are required, for example in large cryogenic air separation units, and which are suitable to be driven by, for example, a steam turbine or electric motor.
  • feed air is passed through a main air compressor (MAC) to attain a desired pressure.
  • Feed air is then cooled and water vapour and other gaseous impurities such as carbon dioxide are removed.
  • Part or all of the feed air stream may then be passed to a booster air compressor (BAC) to attain a desired pressure before the compressed air stream(s) is/are passed to the cryogenic part of the ASU for separation.
  • MAC main air compressor
  • BAC booster air compressor
  • the MAC and BAC usually each comprise more than one compression stage.
  • High flow rate process plant compressors typically comprise centrifugal (i.e . radial) compression stages.
  • the essential features of a centrifugal compression stage include an impeller mounted for rotation within a shaped housing known as a volute or scroll.
  • the compression stage also comprises an inlet and an outlet for the fluid being compressed.
  • Impellers may be arranged either on multiple shafts or on a single shaft. Where multiple shafts are used, a large diameter bull gear drives meshing pinions (i.e . pinion gears) upon the ends of which compression impellers are mounted.
  • the multiple impellers within their own respective housings provide several stages of compression as desired.
  • the bull gear and its meshing pinions are usually contained within a common housing. Consequently, such compressors are known as integral gear compressors.
  • the meshing pinions may have different diameters to best match the speed requirements of the compression impellers they drive.
  • the compressed air between any two stages may be piped to an intercooler, wherein it is cooled,
  • US 5,901,579 discloses a compressor where the main air compression duty is combined on one machine with two compression wheels that share the air coming off the MAC and compresses those streams to feed an air separation plant.
  • FIG. 1 A typical known compression arrangement for use in an air separation unit is depicted in Fig. 1 .
  • This arrangement has been applied for MAC suction flow rates up to 550,000 m 3 /h.
  • the number of booster stages is limited to four.
  • the compressor bull gear 46 of compression arrangement 10 is driven from steam turbine 20 by a drive shafts 30 and 45 and an intermediate gearbox 40. Both the MAC stages 11 and the BAC stages 12 are driven from this bull gear 46.
  • BAC stages There are also four BAC stages (BAC1, BAC2, BAC3 and BAC4), with BAC1 and BAC2 being driven from third pinion 70 and BAC3 and BAC4 being driven from fourth pinion 80.
  • the numbering of the MAC and BAC stages reflects the order in which fluid to be compressed will pass through the stages (i.e . fluid will pass successively through MAC1, MAC2 and MAC3, for example).
  • intercoolers 90, 100, 110, 120 and 130 are provided between the stages to remove heat from the compressed fluid.
  • An aftercooler 140 is provided at the outlet of BAC4 to cool the compressed fluid to the temperature at which it is desired that the fluid enters the air separation unit.
  • the air to be separated is fed into first MAC compression stage MAC1 through inlet 150, is compressed typically to about 0.2 MPa (2 bar absolute or “bara") and leaves MAC1 through pipeline 160 and passes through intercooler 90 before entering second compression stage MAC2 for further compression.
  • the compressed air typically at about 0.35 MPa (3.5 bara), then leaves MAC2 though pipeline 170 and passes through intercooler 100 before entering third compression stage MAC3.
  • the compressed air typically at about 0.6 MPa (6 bara), is then passed to the ASU via outlet 180 for cooling and removal of water vapour and other gaseous impurities such as carbon dioxide.
  • air is passed to the booster compression arrangement 12, entering first booster stage BAC1 by inlet 190 and exiting, typically at about 1.1 MPa (11 bara), though pipeline 200.
  • the compressed air is then passed through intercooler 110 for temperature reduction, and enters second booster compression stage BAC2.
  • the air successively passes through BAC2 outlet pipeline 210, typically at about 2 MPa (20 bara), intercooler 120, third compression stage BAC3, BAC3 outlet pipeline 220, typically at about 3.5 MPa (35 bara), intercooler 130, and fourth booster compression stage BAC4.
  • the compressed air typically at about 5.5 MPa (55 bara) is then passed via pipeline 230 through aftercooler 140 to be brought to the desired temperature and enters the ASU for separation.
  • the BAC 12 is an integrally geared design that may have up to six stages, but an arrangement with only four stages is shown in the figure.
  • Steam turbine 20 is connected to drive shaft 30 and the integrally geared BAC 12 through a speed reducing gearbox 40 and drive shaft 45.
  • the first and second stages (BAC1 and BAC2) of the BAC are driven by pinion gear 70, and the third and fourth stages (BAC3 and BAC4) of the BAC are driven by pinion gear 80.
  • Intercoolers (not shown) are provided between the compression stages.
  • the design of the compressor arrangements of Figs. 1 and 2 limits the impeller diameter of the MAC1 stage due to the impeller weight.
  • the MAC1 volute size is limited to allow the first and second stage volutes to fit on to the gearbox.
  • the impeller of the MAC1 typically has a diameter of 1600 mm which provides the maximum suction flow capacity of 550,000 m 3 /h.
  • MAC suction flow rates up to 800,000m 3 /h an arrangement as shown in Fig. 3 is known and has been developed by Siemens.
  • An integrally geared MAC 11 is driven by the first end of the steam turbine 20 through a first drive shaft 21, an intermediate gearbox 25 and drive shaft 29.
  • the required suction flow capacity is attained by installing two first stage MAC1 on first pinion 50, each MAC1 comprising an impeller having a diameter of 1600 mm.
  • the BAC arrangement 12 is the same as that shown in Fig. 2 .
  • a double ended steam turbine driving such MAC and BAC stages of an ASU has been developed by MAN Diesel and Turbo.
  • a typical compressor and steam turbine arrangement is depicted in Fig. 4 .
  • the steam turbine 20 drives the MAC stages 11 from a first drive shaft 21 at one end of the turbine and the BAC stages 12 from a second drive shaft 30 at the other end of the turbine.
  • the MAC stages 11 are shown here as four stages MAC1, MAC2, MAC3 and MAC4 provided as a single shaft centrifugal air compressor having four impellers. Intercoolers (not shown) are provided within the MAC casing between the stages.
  • This compressor can use a first stage impeller (for MAC1) of a diameter of up to 1900 mm, which permits a maximum suction flow capacity of 670,000 m 3 /h. Since the intercoolers are installed within the MAC casing, the maximum achievable flow rate for this MAC design is limited by the casing weights and dimensions.
  • the BAC stages 12 are arranged on an integral gear driven through a stub shaft arrangement. Four BAC stages are shown, although up to six may be provided.
  • the first and second stages (BAC1 and BAC2) are driven by pinion gear 70 and the third and fourth stages (BAC3 and BAC4) are driven by pinion gear 80.
  • compressor arrangements It would be desirable to reduce the cost and the steam consumption of compressor arrangements compared with known compressor arrangements. In addition, it would be desirable to increase the suction capacity of compressor arrangements, in particular where it is intended that the compressor arrangement is used at high altitude. Further, it would be desirable to simplify the design of compressor arrangements.
  • a compressor arrangement for compressing air comprising:
  • the first stage of the MAC may be driven indirectly by the first drive shaft, for example through an intermediate gearbox.
  • the first stage of the MAC is mounted directly on the first drive shaft and thus is driven directly by the first drive shaft.
  • the first drive shaft may also drive at least one other compression stage.
  • the first drive shaft is dedicated to driving the first stage of the MAC.
  • the first drive shaft preferably drives the first stage of the MAC alone and does not drive any other compression stage.
  • the first stage of the MAC is preferably a centrifugal compression stage. Such a compression stage is also known in the art as a radial compression stage.
  • One advantage of the present invention is that an impeller of any size may be used in the first stage of the MAC. That said, the diameter of the MAC1 impeller is usually at least about 1100 mm. In some preferred embodiments, the MAC1 impeller has a diameter greater than about 1900 mm, e.g . at least about 2000 mm, or even at least about 2100 mm. Theoretically, there is (within reason) no particular limitation on the maximum diameter of the MAC1 impeller although the Inventor acknowledges that there are some practical concerns that limit the size of the MAC1 impeller size. Typically, the MAC1 impeller does not have a diameter of more than about 3000 mm.
  • the compressor arrangement is capable of providing a wide range of maximum suction flow capacities depending on the diameter of the MAC1 impeller.
  • Preferred arrangements provide a maximum suction flow capacity of at least about 200,000 m 3 /h, e.g . greater than 800,000 m 3 /h, or at least about 850,000 m 3 /h, or even at least about 900,000 m 3 /h.
  • the maximum suction flow capacity is no more than about 1,100,000 m 3 /h .
  • the compressor arrangement preferably comprises a volute support and bearing housing for said first drive shaft.
  • the compressor arrangement may be integrated with a cryogenic air separation plant for producing, for example, at least about 1200 mt (metric tons) oxygen per day, e.g . at least about 2000 mt oxygen per day, or at least about 3000 mt oxygen per day, or even at least about 4000 mt oxygen per day.
  • the maximum rate of production of oxygen from a plant using the compression arrangement according to the present invention is about 5000 mt/day.
  • the oxygen production is from about 4000 mt/day to about 4800 mt/day, depending on the altitude of the ASU plant.
  • the MAC may comprise one, two, three or more stages. Where there is an even number of further stages, they are usually mounted in pairs, each pair mounted on a single pinion gear with the further stages of the pair mounted at opposite ends of the pinion gear. In preferred embodiments, the MAC comprises two further stages mounted on opposite ends of a pinion gear.
  • the BAC may comprise from one to ten stages, e.g. from two to eight stages, and preferably either four or six stages.
  • the stages are usually mounted in pairs, each pair on a further pinion gear.
  • the BAC comprises four or six stages arranged in either two or three pairs of stages respectively.
  • Each pair of stages is mounted on a further pinion gear, with the stages mounted on opposite ends of the further pinion gear.
  • intercoolers there may not be any intercoolers to cool the compressed air between the compression stages. However, there may be at least one intercooler, and in preferred embodiments, there is an intercooler after each stage and before the next compression stage, usually with an aftercooler after the final stage.
  • the arrangement of intercoolers depicted in Fig. 1 would be suitable for the present invention, assuming appropriate modification to accommodate driving the first MAC stage directly from the steam turbine 20 rather than the bull gear 46.
  • the driver may comprise any suitable prime mover, for example a steam turbine or an electric motor.
  • a method of compressing feed air for a cryogenic air separation plant comprising:
  • water vapour and/or other gaseous impurities such as carbon dioxide are removed from the further compressed feed air before compression in the BAC.
  • a compressor arrangement 10 is shown in which a steam turbine 20 drives, via a first drive shaft 21, a first MAC stage 11a (MAC1), and, via a second drive shaft 30, second and third MAC stages 11b (MAC 2 and MAC3) and a BAC 12 in four stages (BAC1 to BAC4).
  • MAC1 first MAC stage 11a
  • MAC 2 and MAC3 second and third MAC stages 11b
  • BAC 12 in four stages
  • the first MAC stage, MAC1 alone is directly driven from one end of the steam turbine 20.
  • a volute support and bearing housing 25 is provided to support the shaft and volute of the MAC 11a.
  • the volute support may be of cast or welded construction and is bolted directly to a concrete foundation.
  • the casing of the volute support is designed to locate and take the weight of the volute.
  • the shaft within the volute support transfers the driver torque to the impeller (not shown) and takes the weight of the MAC1 impeller that is bolted directly to the shaft.
  • Radial bearings carry the rotor weight. Thrust bearings locate the rotor axially and carry the impeller thrust loads.
  • the second drive shaft 30 drives the MAC 11b and the BAC 12.
  • MAC1 is a compressor stage comprising an impeller having a diameter of 2100 mm which is larger than can be accommodated on prior art compressor arrangements. This arrangement provides a maximum suction capacity for a single impeller of 800,000 m 3 /h which is typically greater than the prior art arrangements known to the Inventor.
  • the impeller of the MAC1 may have any suitable diameter to provide a desired maximum suction capacity.
  • the diameter of the impeller may be as small as 1100 mm.
  • the diameter of the impeller used in the Example below is 1600 mm.
  • MAC1 and MAC2 are in fluid communication connected by pipeline 160 in which is provided intercooler 90.
  • MAC2 and MAC3 are in fluid communication connected by pipeline 170 in which is provided intercooler 100. Fluid enters MAC1 through inlet 150 and leaves MAC3 to enter the ASU via outlet 180.
  • the pipeline and intercooler arrangement for BAC 12 depicted in Figure 5 is the same as that shown in Fig.1 .
  • the fluid to be compressed enters the MAC1 stage through inlet 150 and is compressed from atmospheric pressure to about 0.2 MPa (2 bara).
  • the compressed fluid exits MAC1 through pipeline 160 and is passed through intercooler 90 to reduce its temperature prior to entry to MAC2 for further compression.
  • the further compressed fluid typically at about 0.35 MPa (3.5 bara), exits MAC2 through pipeline 170 and is passed through intercooler 100 before entering MAC3.
  • the fluid is typically at about 0.6 MPa (6 bara) and is passed to the ASU through outlet 180.
  • the booster compression is as described for Fig. 1 .
  • Fig. 6 shows an alternative compressor arrangement of the invention, in which the MAC 11b and BAC 12 are driven via a pedestal bearing 41 provided in second drive shaft 45 and a stub shaft 90.
  • the arrangement is otherwise as described in Fig. 5 and in use operates in a similar manner.
  • MAC1 stage alone on the first drive shaft removes the size constraint on MAC1 of the prior art arrangements in Figs. 1 to 4 , and so a greater impeller diameter, and therefore greater suction capacity, can be achieved for the MAC.
  • a MAC suction flow rate of at least 800,000 m 3 /h is envisaged. This is of particular importance when operating an ASU at high altitude, in which, due to the lower prevailing atmospheric pressure, a higher suction capacity is required to provide the same ASU production as a similar plant located at sea level.
  • a MAC suction flow rate of 800,000 m 3 /h would provide an ASU with the air required to deliver an oxygen production of between 4000 mt/day and 4800 mt/day depending on the ASU altitude.
  • Fig. 5 and Fig. 6 have a simplified structure compared with Figs. 2 to 4 which permits easier installation and shaft alignment compared with the prior art arrangements of Figs. 2 to 4 .

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP11193001.2A 2011-12-12 2011-12-12 Kompressoranordnung Withdrawn EP2604862A1 (de)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP11193001.2A EP2604862A1 (de) 2011-12-12 2011-12-12 Kompressoranordnung
TW101146156A TW201331463A (zh) 2011-12-12 2012-12-07 一種壓縮機佈置
PCT/EP2012/075044 WO2013087606A1 (en) 2011-12-12 2012-12-11 A compressor arrangement
CN2012206828394U CN203201825U (zh) 2011-12-12 2012-12-12 压缩机布置

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP11193001.2A EP2604862A1 (de) 2011-12-12 2011-12-12 Kompressoranordnung

Publications (1)

Publication Number Publication Date
EP2604862A1 true EP2604862A1 (de) 2013-06-19

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP11193001.2A Withdrawn EP2604862A1 (de) 2011-12-12 2011-12-12 Kompressoranordnung

Country Status (4)

Country Link
EP (1) EP2604862A1 (de)
CN (1) CN203201825U (de)
TW (1) TW201331463A (de)
WO (1) WO2013087606A1 (de)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014180688A1 (de) 2013-05-08 2014-11-13 Voith Patent Gmbh Getriebe und getriebeverdichteranlage
EP2902737A2 (de) 2014-01-24 2015-08-05 Air Products And Chemicals, Inc. Systeme und Verfahren zur Kompression von Luft
US20160230771A1 (en) * 2015-02-06 2016-08-11 Anja Christina DOBAT Geared Turbomachine
EP3236076A1 (de) * 2016-04-20 2017-10-25 Atlas Copco Energas Gmbh Turbomaschinenanordnung
WO2018007029A1 (de) * 2016-07-07 2018-01-11 Man Diesel & Turbo Se Getriebeturbomaschine
EP4163500A1 (de) * 2021-10-11 2023-04-12 Siemens Energy Global GmbH & Co. KG Luftverdichtungsanlage für eine luftzerlegung
EP4163501A1 (de) * 2021-10-11 2023-04-12 Siemens Energy Global GmbH & Co. KG Luftverdichtungsanlage für eine luftzerlegung

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10385861B2 (en) 2012-10-03 2019-08-20 Praxair Technology, Inc. Method for compressing an incoming feed air stream in a cryogenic air separation plant
US10443603B2 (en) 2012-10-03 2019-10-15 Praxair Technology, Inc. Method for compressing an incoming feed air stream in a cryogenic air separation plant

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Publication number Priority date Publication date Assignee Title
US4473754A (en) * 1982-07-26 1984-09-25 Williams International Corporation Waste heat power generation system
DE4416497C1 (de) * 1994-05-10 1995-01-12 Gutehoffnungshuette Man Getriebe-Mehrwellenturbokompressor und Getriebe-Mehrwellenradialexpander
US5485719A (en) * 1991-05-10 1996-01-23 Praxair Technology, Inc. Integration of combustor-turbine units and integral-gear pressure processors
US5901579A (en) 1998-04-03 1999-05-11 Praxair Technology, Inc. Cryogenic air separation system with integrated machine compression

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4473754A (en) * 1982-07-26 1984-09-25 Williams International Corporation Waste heat power generation system
US5485719A (en) * 1991-05-10 1996-01-23 Praxair Technology, Inc. Integration of combustor-turbine units and integral-gear pressure processors
DE4416497C1 (de) * 1994-05-10 1995-01-12 Gutehoffnungshuette Man Getriebe-Mehrwellenturbokompressor und Getriebe-Mehrwellenradialexpander
US5901579A (en) 1998-04-03 1999-05-11 Praxair Technology, Inc. Cryogenic air separation system with integrated machine compression

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10100837B2 (en) 2013-05-08 2018-10-16 Voith Patent Gmbh Transmission and geared compressor system
WO2014180688A1 (de) 2013-05-08 2014-11-13 Voith Patent Gmbh Getriebe und getriebeverdichteranlage
EP2902737A2 (de) 2014-01-24 2015-08-05 Air Products And Chemicals, Inc. Systeme und Verfahren zur Kompression von Luft
US20160230771A1 (en) * 2015-02-06 2016-08-11 Anja Christina DOBAT Geared Turbomachine
EP3236076A1 (de) * 2016-04-20 2017-10-25 Atlas Copco Energas Gmbh Turbomaschinenanordnung
DE102016112453A1 (de) 2016-07-07 2018-01-11 Man Diesel & Turbo Se Getriebeturbomaschine
WO2018007029A1 (de) * 2016-07-07 2018-01-11 Man Diesel & Turbo Se Getriebeturbomaschine
US20190162194A1 (en) * 2016-07-07 2019-05-30 Man Energy Solutions Se Geared Turbo Machine
US10738786B2 (en) 2016-07-07 2020-08-11 Man Energy Solutions Se Geared turbo machine
EP4163500A1 (de) * 2021-10-11 2023-04-12 Siemens Energy Global GmbH & Co. KG Luftverdichtungsanlage für eine luftzerlegung
EP4163501A1 (de) * 2021-10-11 2023-04-12 Siemens Energy Global GmbH & Co. KG Luftverdichtungsanlage für eine luftzerlegung
WO2023061813A1 (de) * 2021-10-11 2023-04-20 Siemens Energy Global GmbH & Co. KG Luftverdichtungsanlage für eine luftzerlegung
WO2023061806A1 (de) * 2021-10-11 2023-04-20 Siemens Energy Global GmbH & Co. KG Luftverdichtungsanlage für eine luftzerlegung

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