EP0348342A1 - Kreiselmaschine mit gegenläufigen Laufrädern und Verwendung der Kreiselmaschine - Google Patents

Kreiselmaschine mit gegenläufigen Laufrädern und Verwendung der Kreiselmaschine Download PDF

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Publication number
EP0348342A1
EP0348342A1 EP89810319A EP89810319A EP0348342A1 EP 0348342 A1 EP0348342 A1 EP 0348342A1 EP 89810319 A EP89810319 A EP 89810319A EP 89810319 A EP89810319 A EP 89810319A EP 0348342 A1 EP0348342 A1 EP 0348342A1
Authority
EP
European Patent Office
Prior art keywords
machine
rotary machine
blades
rotating
blade ring
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Withdrawn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
EP89810319A
Other languages
German (de)
English (en)
French (fr)
Inventor
Dusan Dr. Florjancic
Johann Dr. Riedler
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.)
Sulzer AG
Original Assignee
Sulzer AG
Gebrueder Sulzer AG
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 Sulzer AG, Gebrueder Sulzer AG filed Critical Sulzer AG
Publication of EP0348342A1 publication Critical patent/EP0348342A1/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Withdrawn legal-status Critical Current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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/24—Vanes
    • F04D29/242—Geometry, shape
    • F04D29/245—Geometry, shape for special effects
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F01D5/04—Blade-carrying members, e.g. rotors for radial-flow machines or engines
    • F01D5/041—Blade-carrying members, e.g. rotors for radial-flow machines or engines of the Ljungström type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/003—Having contrarotating parts
    • 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
    • F04D17/127—Multi-stage pumps with radially spaced stages, e.g. for contrarotating type
    • 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
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/445—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps
    • F04D29/447—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps rotating diffusers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D31/00—Pumping liquids and elastic fluids at the same time

Definitions

  • the invention relates to a gyroscope according to the preamble of claim 1. Furthermore, the invention relates to the use of such gyroscopes.
  • Rotary machines are known in which, for example, an axial compressor is connected upstream of a radial impeller.
  • Patent application WO 86/05557 describes such a pump / compressor for multi-phase conveying media, in which a mixer device is connected upstream of the axial compressor.
  • a fixed guide vane ring is arranged immediately following the first stage of the axial compressor and immediately upstream of the counter-rotating blade rings.
  • Such a construction is relatively space-consuming and, in addition, axial compressors have relatively high specific speeds and generate only a slight pressure increase in a wide speed range, which is favorable for the radial compressor connected downstream. A large number of stages are therefore necessary in order to achieve a sufficient pressure increase.
  • the object of the invention is to build a rotary machine which has a sufficient suction head with a compact design.
  • Another object of the invention is to provide a gyroscopic machine which, in particular, also ensures good conveying capacities for conveying multiphase mixtures, such as liquid-gas mixtures.
  • a rotary machine is characterized by the features in the characterizing part of claim 1.
  • the use according to the invention of such rotary machines is characterized in the feature of claim 17.
  • the dependent claims relate to particularly advantageous embodiments and uses of the rotary machine.
  • the design of the centrifugal machine as a radial compressor according to the invention is not a faulty construction, but is, for example, excellently suitable for conveying and compressing multi-phase conveying media, such as liquid-gas mixtures.
  • multi-phase conveying media such as liquid-gas mixtures.
  • Such mixtures which may also contain solid parts in a certain size and quantity, excellent mixing and compression of the compressible gas fractions is initially achieved.
  • segregation hardly occurs if the sub-stages are correctly coordinated.
  • the construction proposed according to the invention can be interpreted as a sequence of several stages, the specific speed of which increases from stage to stage in accordance with the reduction in the gas volume.
  • the formation of the last stage as a rotating diffuser leads to a decrease in the absolute speed of the conveying medium, in that the flow cross section increases in the direction of flow, that is to say radially outwards.
  • Losses in fixed diffusers are relatively high with multi-phase fluids, especially with liquid-gas mixtures.
  • the rotating diffuser has significantly lower losses.
  • fixed parts in zones with higher pressure gradients should be avoided in order to keep power losses in the centrifugal machine low.
  • the efficiency improves if there are no stationary elements in these zones by the Energy exchange losses between the phase components can thus be reduced.
  • the efficiency of the gyroscopic machine i.e. a machine with a more or less radial outflow of the conveyed liquid, for example, a multi-phase pump according to the invention, further increased and improved. Due to the radial outflow, the lowest possible absolute velocity of the fluid is achieved for a given outlet channel width. In such an embodiment, a total pressure increase in the last stage is largely dispensed with in favor of the lowest possible exit velocity of the conveying fluid.
  • Centrifugal machines according to the invention can fundamentally be used to convey a liquid-gas mixture with a change in the percentage composition between 0% and 100% gas (volume percent), the efficiency depending on the design of the centrifugal machine and mixture composition e.g. can vary between 70% and 5%.
  • the efficiency depending on the design of the centrifugal machine and mixture composition e.g. can vary between 70% and 5%.
  • consideration should be given to the impairment of the service life of individual machine parts. The operating range is therefore usually restricted by the required service life of machine parts.
  • a gyroscope for liquid-gas mixtures with a gas content (volume) in the range of approximately 20% to 60% (at the intake pipe inlet of the first stage) is advantageously used.
  • a pressure increase in the range of about 5 to 50 bar or even more can be achieved without further ado.
  • Steps of this type can also have so-called intermediate blades, for example likewise in tandem or multiple blade design.
  • the design according to the invention is suitable for rotary machines with impeller diameters in the range from 100 mm to 1500 mm, preferably in the range from 350 mm to 700 mm.
  • the circumferential speed should be in the range of approximately 80 m / s to 350 m / s if possible.
  • the centrifugal machine 1 designed as a pump and shown in a schematic axial section with the housing 10 has the two counter-rotating impellers 11 and 12.
  • the impeller 11 with the vane carrier disk 110 carries the two vane rings or vane grilles 111 and 112.
  • the impeller 12 with the vane carrier disk 120 carries the vane rings or vane gratings 121 and 122.
  • the vane rings of the two vane carrier disks 110 and 120 are interdigitated.
  • the attachment rotor / inducer 124 is also attached on the suction side.
  • the vane carrier disk 110 forms an inner housing together with the hollow shaft 13.
  • the diffuser 1113 In the area of the radial, outer end of the impeller carrier disk or blade carrier disk 110 is the diffuser 1113, which also rotates with the inner housing.
  • the conveying medium almost radially emerging from the diffuser 1113, enters the annular space 140, in which the deflection grid with the deflection blades 14 is arranged .
  • the delivery medium is thus deflected in the tangential direction, or at least in a direction which deviates from the tangential only by approximately 20 ° to 30 °.
  • the centrifugal machine or pump 2 of FIG. 2 is of conventional design in that it has no rotating inner housing in comparison with that in FIG. 1.
  • the two counter-rotating impellers 21 and 22 are arranged, which are attached to the shafts 25 and 26, respectively.
  • the rotating diffuser 23 is machined in the example of the blade carrier disc 210 shown.
  • the blade carrier disc 210 carries the blade rings 211 and 212 and the carrier disc 220 of the counter-rotating impeller 22 carries the blade rings 222 and 223.
  • the blade rings of the two blade carrier discs 210 and 220 are also arranged here in an interlocking manner.
  • the delivery fluid flows out of the diffuser 23 into the annular space 240 almost radially.
  • the delivery fluid flows out of the diffuser 23 into the annular space 240 almost radially.
  • FIG. 3 shows a schematic side view of the example of an annular space 30, in which a deflection, deflection or dispersion grid 31 with deflection, deflection or dispersion blades 32 is arranged.
  • the deflection takes place up to an angular range of 20 ° to 30 ° to the tangential.
  • FIG. 4 shows in a schematic axial section a gyroscopic machine which comprises three units 41, 42 and 43 arranged one behind the other. While the first, i.e. the input unit 41 is designed as a multi-stage, counter-rotating two-wheel pump, the downstream units 42 and 43 are designed as ordinary centrifugal pumps.
  • FIG. 5 shows a gyroscopic machine, which comprises three units 51, 52 and 53 arranged one behind the other, in a schematic axial section. All three units 51, 52 and 52 are multi-stage, opposing two-wheel turbo machines. This arrangement, as it could be used as a feed pump in a pipeline for oil or for a liquid-oil gas mixture, has additionally installed a turbine stage 54 with the turbine blade rings 541 and 542 in the last multi-stage, opposed two-wheel turbo unit 53.
  • the blade ring 543 contributes to increasing the centripetal pressure and at the same time assumes the function of a stator for the second turbine stage with the blade ring 542.
  • This rotary machine with three units comprises rotating inner housings 511, 521 and 531, which can be connected or coupled as a rotary unit .
  • the return channels of the second stage 52 and possibly also the first stage 51 could be provided with centripetal stages.
  • FIG. 6 shows a schematic axial section of a multi-stage, counter-rotating two-wheel turbomachine 6 with two units 61 and 62 in an encapsulated, double-flow design.
  • the drive machine 63 drives the rotating inner housing 65 and the drive unit 64 the inner rotor 66 equipped with blade rings on both sides.
  • the rotating diffuser 60 is common to the two units 61 and 62 and part of the rotating inner housing 65.
  • FIG. 7 shows the schematic longitudinal section through the rotating inner housing 72 and the counter-rotating inner rotor 73 of a multi-stage, counter-rotating two-wheel turbo unit 7, in which the leading edges 71 of the blades of the first stage are inclined with respect to the flow lines of the conveyed medium.
  • the impeller blades are double-curved. Both constructive measures contribute to an increased and improved homogenization of the phase mixture, e.g. Gas / liquid, at.
  • FIG. 8 schematically shows the supervision of a tandem or multiple blading (multiple blading) as they can be arranged on a blade carrier wheel.
  • intermediate blades 811, 821 and 831 which extend less radially inwards than the blades 81, 82 and 83.
  • All the blades 81, 82, 83 and intermediate blades 811, 821, 831 have intermediate channels Z.
  • the individual blade parts have a type of wing profile in cross section. The use of such constructions can be useful above all, but not only, in the first and possibly the second stage, because it can further improve the homogenization of a multi-phase delivery medium.
  • rotating diffusers and deflection grids in the annular space can also be used in those examples in which no explicit reference has been made. Only a single blade ring or a plurality of blade rings can be arranged on a blade carrier wheel. The number depends solely on the number of stages that a two-wheel compressor has. Likewise, the number of units connected in series can be different from that in the examples shown.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP89810319A 1988-06-23 1989-04-28 Kreiselmaschine mit gegenläufigen Laufrädern und Verwendung der Kreiselmaschine Withdrawn EP0348342A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH2415/88 1988-06-23
CH2415/88A CH678352A5 (ja) 1988-06-23 1988-06-23

Publications (1)

Publication Number Publication Date
EP0348342A1 true EP0348342A1 (de) 1989-12-27

Family

ID=4233267

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89810319A Withdrawn EP0348342A1 (de) 1988-06-23 1989-04-28 Kreiselmaschine mit gegenläufigen Laufrädern und Verwendung der Kreiselmaschine

Country Status (5)

Country Link
EP (1) EP0348342A1 (ja)
JP (1) JPH0315695A (ja)
BR (1) BR8903044A (ja)
CH (1) CH678352A5 (ja)
NO (1) NO892607L (ja)

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1993004288A1 (en) * 1991-08-19 1993-03-04 Framo Developments (Uk) Limited Pump or compressor unit
US5580214A (en) * 1991-12-30 1996-12-03 Framo Developments (Uk) Limited Multiphase fluid treatment
WO1997002407A1 (es) * 1996-04-29 1997-01-23 Abundancia Navarro, Juan Carlos Turbina de gas centrifuga
EP0781929A1 (fr) * 1995-12-28 1997-07-02 Institut Francais Du Petrole Dispositif de pompage ou de compression d'un fluide polyphasique à aubage en tandem
WO1999002864A1 (en) * 1997-07-08 1999-01-21 Technion Research & Development Foundation Ltd. High pressure centrifugal compressor
WO2002068826A2 (en) * 2001-02-23 2002-09-06 Macro-Micro Devices, Inc. Fluid flow controller
CN1093606C (zh) * 1996-10-11 2002-10-30 株式会社不二工机 排水泵
EP2149709A3 (en) * 2008-07-30 2011-10-12 Hitachi Plant Technologies, Ltd. Multistage centrifugal compressor
WO2012007465A1 (de) * 2010-07-15 2012-01-19 Siemens Aktiengesellschaft Zentrifugalverdichter
CN102384111A (zh) * 2011-12-06 2012-03-21 中国石油天然气集团公司 双层叶片气液混输器
US20130136587A1 (en) * 2010-07-28 2013-05-30 Kangyue Technology Co., Ltd. Centrifugal compressor
DE102011121925A1 (de) 2011-12-22 2013-06-27 Robert Bosch Gmbh Verdichter und Verfahren zum Betrieb eines Verdichters
WO2015084926A1 (en) * 2013-12-03 2015-06-11 Flowserve Management Company Rotating diffuser pump
CN106640714A (zh) * 2015-10-28 2017-05-10 熵零股份有限公司 一种对转压缩机
CN112664471A (zh) * 2020-12-25 2021-04-16 西安交通大学 一种双叶轮对旋多翼离心风机
EP4015831A1 (de) * 2020-12-18 2022-06-22 Siemens Energy Global GmbH & Co. KG Radialturbomaschine, insbesondere verdichter

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101816583B1 (ko) * 2016-09-13 2018-01-09 엘지전자 주식회사 배수펌프
CN108730204A (zh) * 2017-04-20 2018-11-02 武保国 一种新型多级离心式压缩机

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE369078C (de) * 1923-02-14 Eugen Haber Vorrichtung zum Foerdern von Fluessigkeiten, Luft oder Gasen mittels Schleudergeblaese
DE564826C (de) * 1932-11-23 Siemens Schuckertwerke Akt Ges Einrichtung zur Foerderung von Gasen oder Fluessigkeiten mit einem Schraubenrad im Einlaufkanal eines Fliehkraftrades und zwischen Schrauben- und Fliehkraftrad eingeschaltetem, von innen nach aussen durchstroemtem Diffusor
US2318990A (en) * 1942-06-10 1943-05-11 Gen Electric Radial flow elastic fluid turbine or compressor
GB583469A (en) * 1943-01-04 1946-12-19 David Macleish Smith Improvements in turbo compressors
FR1181043A (fr) * 1957-08-09 1959-06-11 Snecma Pompe centrifuge contrarotative perfectionnée
DE1110810B (de) * 1956-01-19 1961-07-13 Licentia Gmbh Gegenlauf-Verdichter oder -Pumpe
US3044685A (en) * 1959-02-13 1962-07-17 Nicholas P Lapiken Air compressor
GB2193533A (en) * 1986-08-06 1988-02-10 Nuovo Pignone Spa Centrifugal pump particularly for pumping fluids with a high gas content

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE369078C (de) * 1923-02-14 Eugen Haber Vorrichtung zum Foerdern von Fluessigkeiten, Luft oder Gasen mittels Schleudergeblaese
DE564826C (de) * 1932-11-23 Siemens Schuckertwerke Akt Ges Einrichtung zur Foerderung von Gasen oder Fluessigkeiten mit einem Schraubenrad im Einlaufkanal eines Fliehkraftrades und zwischen Schrauben- und Fliehkraftrad eingeschaltetem, von innen nach aussen durchstroemtem Diffusor
US2318990A (en) * 1942-06-10 1943-05-11 Gen Electric Radial flow elastic fluid turbine or compressor
GB583469A (en) * 1943-01-04 1946-12-19 David Macleish Smith Improvements in turbo compressors
DE1110810B (de) * 1956-01-19 1961-07-13 Licentia Gmbh Gegenlauf-Verdichter oder -Pumpe
FR1181043A (fr) * 1957-08-09 1959-06-11 Snecma Pompe centrifuge contrarotative perfectionnée
US3044685A (en) * 1959-02-13 1962-07-17 Nicholas P Lapiken Air compressor
GB2193533A (en) * 1986-08-06 1988-02-10 Nuovo Pignone Spa Centrifugal pump particularly for pumping fluids with a high gas content

Cited By (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1993004288A1 (en) * 1991-08-19 1993-03-04 Framo Developments (Uk) Limited Pump or compressor unit
US5580214A (en) * 1991-12-30 1996-12-03 Framo Developments (Uk) Limited Multiphase fluid treatment
EP0795689A1 (en) * 1991-12-30 1997-09-17 Framo Developments (U.K.) Limited Multiphase fluid treatment
EP0781929A1 (fr) * 1995-12-28 1997-07-02 Institut Francais Du Petrole Dispositif de pompage ou de compression d'un fluide polyphasique à aubage en tandem
FR2743113A1 (fr) * 1995-12-28 1997-07-04 Inst Francais Du Petrole Dispositif de pompage ou de compression d'un fluide polyphasique a aubage en tandem
US5885058A (en) * 1995-12-28 1999-03-23 Institute Francais Du Petrole Multiphase fluid pumping or compression device with blades of tandem design
US6149385A (en) * 1995-12-28 2000-11-21 Institut Francais Du Petrole Multiphase fluid pumping or compression device with blades of tandem design
WO1997002407A1 (es) * 1996-04-29 1997-01-23 Abundancia Navarro, Juan Carlos Turbina de gas centrifuga
CN1093606C (zh) * 1996-10-11 2002-10-30 株式会社不二工机 排水泵
WO1999002864A1 (en) * 1997-07-08 1999-01-21 Technion Research & Development Foundation Ltd. High pressure centrifugal compressor
US6589013B2 (en) 2001-02-23 2003-07-08 Macro-Micro Devices, Inc. Fluid flow controller
WO2002068826A3 (en) * 2001-02-23 2003-04-17 Macro Micro Devices Inc Fluid flow controller
WO2002068826A2 (en) * 2001-02-23 2002-09-06 Macro-Micro Devices, Inc. Fluid flow controller
EP2149709A3 (en) * 2008-07-30 2011-10-12 Hitachi Plant Technologies, Ltd. Multistage centrifugal compressor
WO2012007465A1 (de) * 2010-07-15 2012-01-19 Siemens Aktiengesellschaft Zentrifugalverdichter
US9347450B2 (en) * 2010-07-28 2016-05-24 Kangyue Technology Co., Ltd. Centrifugal compressor
US20130136587A1 (en) * 2010-07-28 2013-05-30 Kangyue Technology Co., Ltd. Centrifugal compressor
CN102384111B (zh) * 2011-12-06 2013-09-04 中国石油天然气集团公司 双层叶片气液混输器
CN102384111A (zh) * 2011-12-06 2012-03-21 中国石油天然气集团公司 双层叶片气液混输器
WO2013092982A1 (de) 2011-12-22 2013-06-27 Robert Bosch Gmbh Verdichter und verfahren zum betrieb eines verdichters
DE102011121925A1 (de) 2011-12-22 2013-06-27 Robert Bosch Gmbh Verdichter und Verfahren zum Betrieb eines Verdichters
WO2015084926A1 (en) * 2013-12-03 2015-06-11 Flowserve Management Company Rotating diffuser pump
US20160305447A1 (en) * 2013-12-03 2016-10-20 Flowserve Management Company Rotating diffuser pump
US11396887B2 (en) 2013-12-03 2022-07-26 Flowserve Management Company Rotating diffuser pump
CN106640714A (zh) * 2015-10-28 2017-05-10 熵零股份有限公司 一种对转压缩机
EP4015831A1 (de) * 2020-12-18 2022-06-22 Siemens Energy Global GmbH & Co. KG Radialturbomaschine, insbesondere verdichter
CN112664471A (zh) * 2020-12-25 2021-04-16 西安交通大学 一种双叶轮对旋多翼离心风机

Also Published As

Publication number Publication date
NO892607L (no) 1989-12-27
CH678352A5 (ja) 1991-08-30
JPH0315695A (ja) 1991-01-24
BR8903044A (pt) 1990-02-06
NO892607D0 (no) 1989-06-22

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