EP4384714A1 - Compresseur, en particulier compresseur radial - Google Patents

Compresseur, en particulier compresseur radial

Info

Publication number
EP4384714A1
EP4384714A1 EP22786802.3A EP22786802A EP4384714A1 EP 4384714 A1 EP4384714 A1 EP 4384714A1 EP 22786802 A EP22786802 A EP 22786802A EP 4384714 A1 EP4384714 A1 EP 4384714A1
Authority
EP
European Patent Office
Prior art keywords
compressor
liquid
impeller
injected
injection
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.)
Pending
Application number
EP22786802.3A
Other languages
German (de)
English (en)
Inventor
Bouchaib El-Haissouk
Viktor Hermes
Jörg Rheims
Axel Spanel
Christian Woiczinski
Attilla Yildiz
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.)
Siemens Energy Global GmbH and Co KG
Original Assignee
Siemens Energy Global GmbH and Co KG
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 Siemens Energy Global GmbH and Co KG filed Critical Siemens Energy Global GmbH and Co KG
Publication of EP4384714A1 publication Critical patent/EP4384714A1/fr
Pending legal-status Critical Current

Links

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
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4213—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps suction ports
    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/70—Suction grids; Strainers; Dust separation; Cleaning
    • F04D29/701—Suction grids; Strainers; Dust separation; Cleaning especially adapted for elastic fluid pumps
    • F04D29/705—Adding liquids

Definitions

  • Compressors in particular centrifugal compressors
  • the invention relates to a compressor, in particular a centrifugal compressor.
  • water injection is used in raw gas compressors, where the water is injected between the compressor stages in order to reduce the outlet temperature of the medium between the individual stages in order to prevent the medium from polymerisation.
  • the limiting degree of vaporization of the liquid injected into the compressor gas stream is problematic. If the liquid is injected into a low velocity area of the compressor, breaking up or atomizing the liquid into very small droplets may not be achieved. Very small droplets are necessary to achieve a high degree of vaporization len, because the surface area of such a droplet is large in relation to the volume of the droplet and the droplet can so easily absorb heat and evaporate.
  • the object of the invention is to specify an improved compressor, in particular a radial compressor.
  • a compressor comprising a rotor which extends along an axis of rotation, a housing, the housing being arranged around the rotor, the housing having an axial inflow and downstream of the axial inflow a first compression stage and further downstream of the first Compression stage has a first radial outflow for a process fluid, the first radial outflow leading through the inner housing, furthermore an impeller, which is arranged on the rotor, with an injection device for injecting a liquid into the axial inflow, the process fluid to be compressed is first sucked in and the quantity of injected liquid depends on the temperature and relative humidity of the sucked-in medium.
  • a compression stage means the compression of a specific mass flow by means of one or more compressor impellers.
  • compressor stage or “compression stage” according to the invention is the compression taking place in an uninterrupted flow path in the compressor, without the compression to be compressed Mass flow or a partial flow thereof is derived from the compressor and possibly. is subjected to other process steps.
  • a mixture is used as the liquid.
  • a further improvement consists in using suitable mixing partners to produce a higher boiling point if this is beneficial to the compression process. Also, mixing could occur within the medium to be compressed if the enthalpy of mixing is negative and additional (mixing) cooling is to be achieved.
  • the aim of the invention is also to approach isothermal compression, which leads to high efficiency.
  • a liquid according to the invention such as e.g. B. Water or LPG
  • the volume flow of the flow can be reduced.
  • the speed and the flow losses decrease. In this way, evaporation can be used to make compressors more compact, without the negative consequences of compactness on the performance of the compressor.
  • injection in the spiral stage (last stage of a process stage) is particularly effective.
  • an injection device is also proposed in inlets and return stages.
  • the amount of liquid should be regulated to ensure an optimal condition close to saturation and to avoid liquid accumulation.
  • the amount of water is about 2 wt. -% . This reduces the total volume flow incl. Evaporated added water by about 8% which should reduce losses from a diffuser and coil by about 15%.
  • Either a gas in the liquid aggregate state can be injected or another medium such as e.g. B. Water, methanol or ethanol, or a mixture of several components.
  • the injected medium is selected so that its evaporation temperature is lower than the temperature at the impeller outlet of the subsequent compression stage without liquid injection, based on the final pressure there.
  • the evaporation temperature in the case of mixtures: the lowest-boiling component
  • the gas temperature at the point of injection can be lower than the gas temperature at the point of injection.
  • the injected medium is selected in such a way that the evaporation temperature is above the temperature of the compressed gas at the point of injection and below the temperature after the subsequent compressor stage, based on the case without liquid injection.
  • Active dosing of the amount of liquid improves liquid injection.
  • the amount of liquid is calculated using the temperature and the relative humidity of the sucked-in medium.
  • the dosing can then be done by switching nozzles on and off or via the pump speed or also via a by-pass control.
  • the dwell time with the injected liquid plays a decisive role in the effective humidification of the process fluid.
  • a minimum distance between an injection and an impeller inlet of 3 times the impeller inlet diameter is proposed in order to achieve an effective reduction in the compressor drive power by means of liquid injection.
  • the distance between the injection and the impeller inlet is essentially 10 times the impeller inlet diameter.
  • the relationship applies that the distance between the injection and the impeller inlet can be smaller, the finer the liquid droplets that are introduced.
  • a cascading of the injection in several units with a defined distance from one another is proposed.
  • the minimum distance of the last cascade should not be undershot.
  • the injection nozzles in the cascade can be offset from one another, viewed in the direction of flow, in order not to interfere with one another. In a cascaded arrangement, the quantity of liquid injected per position can be reduced.
  • FIG. 1 shows a sectional illustration of a radial compressor according to the prior art
  • Figure 2 is a longitudinal section through a schematic Representation of a first compressor according to the invention
  • FIG. 1 shows a known radial flow machine in a (simplified) sectional view.
  • the flow machine shown is a compressor 1, in particular a centrifugal compressor.
  • the turbomachine includes, among other things, a radial impeller 2 which is mounted such that it can rotate about an axis of rotation 3 .
  • the impeller 2 has an axial inflow 4 and a radial outflow 5 .
  • the impeller 2 comprises a hub 6 and impeller blades 7 protruding radially from the hub 6 .
  • Flow channels through which a fluid can flow are formed between the impeller blades 7 .
  • the hub 6 is connected to a shaft of the compressor 1 that is not shown in the figure.
  • the impeller 2 has a wheel disc 8 which is formed in one piece with the hub 6 and connects the impeller blades 7 to one another.
  • the impeller 2 is a so-called open impeller, ie an impeller without a cover plate.
  • the impeller 2 could be a so-called closed impeller, ie an impeller with a cover disk.
  • the compressor 1 comprises a housing 9 in which the impeller 2 is placed.
  • a part of the housing 9 is designed as a volute housing. That is, the housing 9 has a NEN spiral housing part 10 with a spiral cavity 11 on.
  • the compressor has an annular diffuser 12 which is axially symmetrical with respect to the axis of rotation 3 and which is designed as a hollow chamber or as a channel in the housing 9 .
  • the diffuser 12 is arranged around a circumference of the impeller 2 and is designed as a radial diffuser.
  • the diffuser 12 opens into the spiral housing part 10 or into its cavity 11.
  • FIG. 1 an outlet diameter 13 of the impeller 2 is shown in FIG. 1 in the form of a double arrow.
  • the diffuser 12 has a plurality of diffuser vanes 14 . That is, diffuser 12 is a vaned diffuser. In the present exemplary embodiment, the diffuser 12 has six diffuser vanes 14, only two of which can be seen in FIG. In principle, however, the diffuser 12 could also have a different number of diffuser vanes 14 .
  • the compressor 1 is used to compress a fluid such as air.
  • a fluid such as air.
  • the fluid flows axially through the axial inflow 4 into the impeller 2 or into the flow channels formed by the impeller blades 7.
  • the fluid is set in rotation by the impeller 2 and leaves the impeller 2 radially outwards through the radial outflow 5.
  • the diffuser 12 converts part of the kinetic energy of the fluid into potential energy in the form of pressure and guides the fluid into the cavity 11 of the volute casing part 10.
  • FIG. 2 shows a longitudinal section of a schematic representation of a part of the compressor 1 with an inventive according injection device 15 .
  • Part of the axial inflow 4 can be seen on the left-hand edge of FIG.
  • An impeller inlet diameter 16 is indicated by the double arrow.
  • the impeller inlet 17 is arranged in front of the impeller 2, which is not shown in FIG.
  • An inflow housing 18 is arranged at the impeller inlet 17 and is connected to one another via a plurality of flanges 19 .
  • a nozzle 21 is arranged at a distance 20 in the inflow housing 18 .
  • the nozzle 21 is designed to supply liquid.
  • a process fluid flowing from the right is moved in the direction of the compressor 1 and a liquid enters the process fluid by means of the nozzles 21 .
  • the evaporation temperature of the liquid is lower than the temperature of the process fluid to be compressed after injection in the compression process.
  • the injection device 15 has a control device, not shown in detail, which is designed in such a way that the quantity of injected liquid can be controlled.
  • the injection device 15 is designed in such a way that the process fluid to be compressed is first sucked in and the quantity of injected liquid depends on the temperature and relative humidity of the sucked-in process fluid.
  • the injection device 15 is designed in such a way that the liquid is injected within the process fluid to be compressed.
  • the injection device 15 can have a plurality of nozzles 21 (not shown), which are arranged one behind the other in the direction of flow of the process fluid. It has been shown that the injection effect is advantageous if the distance 20 between the last nozzle 21 in front of the impeller 2 and the impeller inlet 17 is three times the impeller inlet diameter 16 .
  • a further advantageous effect is seen when the distance 20 between the last nozzle 21 in front of the impeller 2 and the impeller inlet 17 is 0.5 to 0.75 times, preferably 0.66 times, the impeller inlet diameter 16 .
  • the injection device 15 is particularly effective when the distance 20 between the last nozzle 21 in front of the impeller 2 and the impeller inlet 17 is 10 times the impeller inlet diameter 16 .
  • a further possibility of improving the effectiveness of the injection device 15 is achieved by arranging a plurality of nozzles one behind the other in the direction of flow. Improved mixing is possible as a result. This improved arrangement is shown schematically in FIG. 2 by a first line 23 and a second line 24 .
  • Further nozzles are arranged both on the first line 23 and on the second line 24 .
  • the distance between the nozzles 21 and the position corresponding to 10 times the distance 22 is the length L.
  • the distance between the nozzle 21 and the further nozzle at the position on the first line 23 corresponds essentially to one third of the length L .
  • the distance between the further nozzles at the first position 23 and the further nozzles at the position on the second line 24 corresponds essentially to one third of the length L .
  • the distance between the further nozzles at the second position 24 and the position corresponding to 10 times the distance 22 is essentially one third of the length L . Only two further positions for further nozzles are shown in FIG. Other nozzles that are arranged at a distance from one another are also conceivable.

Landscapes

  • 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)

Abstract

L'invention concerne un compresseur (1) comprenant un rotor s'étendant le long d'un axe de rotation (3), un boîtier (9) disposé autour du rotor, le boîtier (9) présentant un flux entrant axial (4) et, en aval du flux entrant axial (4), un premier étage de compression et, plus loin en aval du premier étage de compression, un flux sortant radial (5) pour un fluide de traitement, le flux sortant radial (5) traversant le boîtier (9), et comprenant encore une roue (2) disposée sur le rotor, avec un dispositif d'injection (15) pour injecter un fluide dans le flux entrant axial (4).
EP22786802.3A 2021-10-21 2022-09-22 Compresseur, en particulier compresseur radial Pending EP4384714A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP21203945.7A EP4170186A1 (fr) 2021-10-21 2021-10-21 Compresseur, en particulier compresseur radial
PCT/EP2022/076327 WO2023066585A1 (fr) 2021-10-21 2022-09-22 Compresseur, en particulier compresseur radial

Publications (1)

Publication Number Publication Date
EP4384714A1 true EP4384714A1 (fr) 2024-06-19

Family

ID=78371825

Family Applications (2)

Application Number Title Priority Date Filing Date
EP21203945.7A Withdrawn EP4170186A1 (fr) 2021-10-21 2021-10-21 Compresseur, en particulier compresseur radial
EP22786802.3A Pending EP4384714A1 (fr) 2021-10-21 2022-09-22 Compresseur, en particulier compresseur radial

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP21203945.7A Withdrawn EP4170186A1 (fr) 2021-10-21 2021-10-21 Compresseur, en particulier compresseur radial

Country Status (5)

Country Link
US (1) US20240410378A1 (fr)
EP (2) EP4170186A1 (fr)
JP (1) JP2024537237A (fr)
CN (1) CN118119771A (fr)
WO (1) WO2023066585A1 (fr)

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2877098B2 (ja) * 1995-12-28 1999-03-31 株式会社日立製作所 ガスタービン，コンバインドサイクルプラント及び圧縮機
JP2000120596A (ja) * 1998-10-12 2000-04-25 Ishikawajima Harima Heavy Ind Co Ltd ターボ圧縮機用の水噴霧装置
AU2003224986A1 (en) * 2002-04-15 2003-11-03 Mee Industries, Inc. Water injection for gas turbine inlet air
AU2002342497A1 (en) * 2002-06-13 2003-12-31 Alstom Technology Ltd Method for operating a gas turbine installation, and gas turbine installation
US7028485B1 (en) * 2002-10-02 2006-04-18 Mee Industries, Inc. Surge prevention for compressor inlet air fogging
DE10340177A1 (de) * 2003-09-01 2005-03-31 Alstom Technology Ltd Zerstäubungs- und Eindüsensystem, und Verfahren zum Betrieb
US7252474B2 (en) * 2003-09-12 2007-08-07 Mes International, Inc. Sealing arrangement in a compressor
JP5190653B2 (ja) * 2007-11-14 2013-04-24 国立大学法人名古屋大学 圧縮機
JP2009191635A (ja) * 2008-02-12 2009-08-27 Ihi Corp ガス機械
JP2011111990A (ja) * 2009-11-27 2011-06-09 Mitsubishi Heavy Ind Ltd 遠心圧縮機
CH705323A1 (de) * 2011-07-25 2013-01-31 Alstom Technology Ltd Verfahren zum Einspritzen von Wasser in einen mehrstufigen Axialverdichter einer Gasturbine.
CA3006624C (fr) * 2015-12-11 2020-07-21 Atlas Copco Airpower, Naamloze Vennootschap Procede de controle de l'injection de liquide d'un dispositif compresseur ou d'expansion, dispositif compresseur ou d'expansion a injection de liquide et un element compresseur oud'expansion a injection de liquide
JP6620644B2 (ja) * 2016-03-31 2019-12-18 株式会社豊田自動織機 遠心圧縮機
EP3441621A1 (fr) * 2017-08-10 2019-02-13 Siemens Aktiengesellschaft Turbocompresseur avec injection de gaz de compression liquéfié dans l'écoulement
CN107559239B (zh) * 2017-09-20 2019-03-26 北京航空航天大学 一种具有中心喷嘴结构的离心气体压缩机减温器
FR3088679B1 (fr) * 2018-11-16 2020-12-11 Safran Helicopter Engines Circuit d'injection de fluide en amont d'une turbomachine

Also Published As

Publication number Publication date
EP4170186A1 (fr) 2023-04-26
WO2023066585A1 (fr) 2023-04-27
JP2024537237A (ja) 2024-10-10
US20240410378A1 (en) 2024-12-12
CN118119771A (zh) 2024-05-31

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