EP0301285A1 - Zentrifugalkompressor - Google Patents

Zentrifugalkompressor Download PDF

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Publication number
EP0301285A1
EP0301285A1 EP88110809A EP88110809A EP0301285A1 EP 0301285 A1 EP0301285 A1 EP 0301285A1 EP 88110809 A EP88110809 A EP 88110809A EP 88110809 A EP88110809 A EP 88110809A EP 0301285 A1 EP0301285 A1 EP 0301285A1
Authority
EP
European Patent Office
Prior art keywords
gas
axles
axle
casing
centrifugal
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.)
Granted
Application number
EP88110809A
Other languages
English (en)
French (fr)
Other versions
EP0301285B1 (de
Inventor
Kazuzo C/O Hiroshima Machinery Works Katayama
Yasutoshi C/O Hiroshima Machinery Works Hirayama
Susumu C/O Hiroshima Machinery Works Izaki
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.)
Mitsubishi Heavy Industries Ltd
Original Assignee
Mitsubishi Heavy Industries Ltd
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 Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Publication of EP0301285A1 publication Critical patent/EP0301285A1/de
Application granted granted Critical
Publication of EP0301285B1 publication Critical patent/EP0301285B1/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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/058—Bearings magnetic; electromagnetic
    • 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
    • F04D17/122—Multi-stage pumps the individual rotor discs being, one for each stage, on a common shaft and axially spaced, e.g. conventional centrifugal multi- stage compressors
    • 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
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/051—Axial thrust balancing
    • 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
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/053—Shafts
    • F04D29/054—Arrangements for joining or assembling shafts
    • 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

Definitions

  • the present invention relates to a centrifugal compressor in a gas compressing system available in the field of the petrochemistry or the like.
  • a capability of raising a pressure with one stage of impeller has a limit, and in the case where a high pressure ratio or a high pressure head is required, a multi-stage arrangement is employed.
  • the number of stages of impellers that can be accommodated within a single casing is limited in order to insure rigidity of an axle and to realize safe operations. Accordingly, in the prior art, in the case where a high pressure head was required, it was realized by arraying a plurality of casings either in series or in parallel.
  • Fig. 3 illustrates one example of the arrangement in the prior art, in which in order to realize a high pressure head, a gas compressing system was constructed by arraying three casings of a first compressor 49, a second compressor 50 and a third compressor 51 in series as numbered sequentially from the suction side.
  • the interior of the individual compressor casing is composed of a multiple stages of centrifugal compressors.
  • Driving power fed from a driving machine is transmitted via a drive shaft 57, and it is distributed from the third compressor 51 to the second compressor 50, and from the second compressor 50 to the first compressor 49, respectively by the inter­mediary of an intermediate coupling.
  • An intake gas is sucked through a gas suction pipe 41, then it is compressed by the first compressor 49, and it is delivered through a gas delivery pipe 42.
  • the delivered gas passes through an intermediate gas cooler 43, in which heat-exchange is effected between the gas and a coolant water introduced from the outside through a coolant water feed pipe 58, and thereby the gas is cooled.
  • the gas is sucked through a gas suction pipe 44 of the second compressor 50, and it is delivered through a gas delivery pipe 45.
  • the gas cooled by an intermediate gas cooler 46 in a similar manner is sucked through a gas suction pipe 47 and compressed by the third compressor 51, then it is delivered from a final gas delivery port 48, and it is used as a high-pressure gas.
  • bearings are disposed in the proximities of the opposite axial end surfaces of the casing, and in order to prevent the gas enclosed within the casing from leaking out, gas seal means are disposed at the locations where the drive shaft penetrates the end plates of each casing.
  • sealing oil feed tubes 52, 53 and 54 are constructed so as to follow the change of the pressure within the casing, if the feed of sealing oil should become faulty, the sealing capability would be lost, and hence, the gas seal means per se as well as the sealing oil feed mechanism are respectively required to individual­ly have a high reliability, and their manufacturing expense would become high.
  • lubricant oil is fed to the bearings through a lubricant oil feed tube 55, and drain oil in the bearing boxes is drained through a lubricant oil pipe 56.
  • a more specific object of the present invention is to provide a centrifugal compressor, in which stable operations over a long period time can be insured in an economical manner.
  • Another object of the present invention is to provide a centrifugal compressor which does not neces­sitate a large number of seal means.
  • Yet another object of the present invention is to provide a centrifugal compressor which can be construct­ed in a less expensive matter without necessitating expensive materials nor machining at a high precision.
  • Still another object of the present invention is to provide a centrifugal compressor which does not necessitate a complicated mounting structure for main­taining axial alignment of a plurality of axles having impellers thereon.
  • a centrifugal compressor comprising a plurality of axles each having centrifugal impellers that can compress gas by making use of a centrifugal force exerted upon the gas, electromagnetic bearings for support­ing the axles at their opposite ends without being held in contact with the axles, coupling means for coupling the axles with one another as arrayed in series sequentially in such order that said gas can be compressed towards one side, in such manner that misalignment of their axes with one another may be allowed, a casing for supporting the plurality of coupled axles integrally with the electro­magnetic bearings therefor and having a suction port of gas at one end in the axial direction and a delivery port thereof at the other end, and seal means around the axle provided on the side having the delivery port of the casing.
  • centrifugal compressor wherein a gas cooling section for cooling the gas compressed by the centrifugal impellers on the axles, is mounted to the casing.
  • the first-featured centrifugal compressor wherein a suction magnetic bearing for sucking the axle on the gas suction side towards the gas delivery side is provided, and the electromagnetic bearing on the gas delivery side is a thrust bearing for holding the axle on the gas delivery side at a predeter­mined position in its axial direction.
  • the coupling means is composed of restraining shafts mounted to the adjacent axial ends of the axles so as to oppose to each other, two flexible discs disposed around the restraining shafts and respec­tively mounted to the respective axles, and a torque transmission tube connected to the flexible discs.
  • the present invention owing to the above-described construction that a plurality of axles are disposed in series within a single casing and the respec­tive axles are supported by magnetic bearings at their opposite ends, bearing oil is not necessitated. And, by disposing the bearings in the gas, the location where the axle penetrates through the end surface on the high pres­sure side of the casing becomes only one location on the side for transmitting driving power, and so, the number of places where counter-measure for leakage of gas must be taken is greatly reduced, and high reliability can be realized.
  • This gas passes along the outer circumference of a bearing body supporting the axle 3, and while it is being compressed by a multiple stages of centrifugal impellers, it is delivered from the last stage centrifugal impeller mounted to the axle 3, and it flows out through a first delivery port 38.
  • the gas flows into a gas cooling section 4 mounted on the outer circumference of the casing 1, where it passes through the interstices in a cooling tube group 6 which is cooled by an externally supplied coolant water 5, and after it has been cooled down to a predetermined temperature, it is led to a gas suction port 8 of a multi-stage compressor assembly mounted to a second axle 7.
  • the gas compressed again and delivered through a delivery port 9 is again introduced into the gas cooling section 4 on the outer circumference of the casing 1, and it is cooled there.
  • the gas side chamber in the gas cooling section 4 is partitioned into two chambers for use with the axle 3 and for use with the axle 7.
  • the cooled gas is again intro­duced to a gas suction port 10 of a multi-stage compressor assembly constructed by a third axle 12, and it is again compressed there by a compressing action consisting of the action of the impeller and the already known diffuser effect, in combination.
  • the gas compressed up to the final stage is delivered through a final delivery port 11 at a predetermined pressure.
  • a compressor assembly composed of a plurality of axles 3, 7 and 12 each having impellers mounted thereon, and a stationary member for forming gas passageways to properly compress gas.
  • the axle 3 is supported by radial bearings 13 and 14, the axle 7 is supported by radial bearings 15 and 16, the axle 12 is supported by radial bearings 17 and 18, and all these axles are supported independently in a non-­ contact manner by an electromagnetic effect making use of magnets. Since these bearings do not necessitate lubricant oil as is the case with the bearings in the prior art, they could be disposed even in gas without being accom­panied by any problem.
  • the respective axles 3, 7 and 12 are connected with each other via an intermediate coupling 19 as will be described later, and a necessary torque is transmitted through the intermediate coupling 19.
  • This intermediate coupling 19 has the function that it allows relative displacement in the radial direction freely among the axles 3, 7 and 12, but among the relative displacement in the axial direction, it restrains the relative dis­placement in the direction of the respective axles ap­proaching to each other.
  • the compressor can tightly seal the gas by disposing a gas seal device 23 for preventing gas within the casing from leaking out to the outside, only at the location where the third axle 12 for transmitting a torque transmitted from the drive coupling 20 to the respective axles 3, 7 and 12 within the casing 1, penetrates the casing end plate 22 forming a part of the casing 1.
  • the number of locations of gas seal devices is remarkably reduced.
  • a pressure balancing disc 25 mounted to the axle 12, and a high-pressure gas is reduced in pressure toward a pressure balancing chamber 24 via labyrinth fins to make the gaseous forces in the axial directions applied to the axle 12 appropriately balance with each other.
  • the pressure balancing chamber 24 is connected through a pressure balancing tube 21 additionally provided on a casing end plate 22 to a low-pressure environment at the gas suction port 2.
  • a thrust collar 28 At one end of the axle 12 is additionally provided a thrust collar 28, an electromagnetic thrust bearing 29 sandwiching this thrust collar 28 from the opposite sides in the axial direction is fixedly secured to the stationary side, and this electromagnetic thrust bearing 29 operates to detect the position in the axial direction of the axle 12 via a control device disposed externally and to return the axle 12 to a predetermined position.
  • a suction magnetic bearing 27 is provided on the back surface of an impeller 26 which achieves initial gas suction effects. The suction force of this suction magnetic bearing 27 acts upon the first axle 3 and the second axle 7.
  • this suction magnetic bearing 27 By making this suction magnetic bearing 27 have a capability of generating a suction force exceeding the sum of the un­balanced forces caused by gas pressure directed towards the gas suction port, the first and second axles 3 and 7 are always applied with a force tending to move them towards the gas delivery side. Since the intermediate coupling 19 has a structure adapted to prevent the axles from approaching to each other as described above, this force is transmitted to the third axle 12, but as the position in the axial direction of the axle 12 is con­trolled by the action of the electromagnetic thrust bearing 29, the axles 3, 7 and 12 are all fixed in posi­tion in the axial direction, and so, their relative positions with respect to the stationary structure are maintained at predetermined positions.
  • the object to be sucked need not be the impeller 26, but so long as it is a disc-­shaped one rotatable integrally with the axle, anything could be employed, and in essence, if the object is adapt­ed to generate a force based on a magnetic effect which sucks the first axle 3 towards the delivery port side, the desired purpose can be achieved.
  • a torque transmission tube 33 is coupled to flanges formed on these hubs via thin flexible discs 32, by means of bolts and nuts 35.
  • Reference numeral 34 designates a protective plate for the flexible disc 32.
  • restraining shafts 36 and 37 To the axial ends of the axles 3 and 7 are mounted restraining shafts 36 and 37, respectively, directed in the axial direction.
  • the restraining shaft 36 has a projection 39 at the center of its axial end surface, so that in the case where the respective restraining shafts 36 and 37 come into contact with each other, the contact is made at the center of their end surfaces and the respec­tive axles cannot approach further to each other.
  • the axles 3 and 7 would not move in the direction of approach­ing to each other during the operation, and even if their rotary axes should become misaligned, no reaction force is generated in the radial direction thanks to the flex­ibility of the flexible discs 32 and the torque transmis­sion tube 33, so that smooth torque transmission can be achieved.
  • casing 1 is illustrated in Fig. 1 so as to be divided into parts forming gas passageways and an outside box-like part for integrally holding these parts (applied with differently directed hatchings), as a matter of course, there is no need to divide into these parts, but so long as it is possible in view of the manufacturing technique, for instance, the casing could be formed integrally as by casting.
  • the inter­mediate coupling also need not be limited to the illus­trated structure, but so long as relative misalignment between the axes of the respective axles is permissible, any other structure could be employed.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Electromagnetism (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP88110809A 1987-07-23 1988-07-06 Zentrifugalkompressor Expired - Lifetime EP0301285B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP182299/87 1987-07-23
JP62182299A JPH076518B2 (ja) 1987-07-23 1987-07-23 遠心圧縮機

Publications (2)

Publication Number Publication Date
EP0301285A1 true EP0301285A1 (de) 1989-02-01
EP0301285B1 EP0301285B1 (de) 1991-10-02

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ID=16115859

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88110809A Expired - Lifetime EP0301285B1 (de) 1987-07-23 1988-07-06 Zentrifugalkompressor

Country Status (4)

Country Link
EP (1) EP0301285B1 (de)
JP (1) JPH076518B2 (de)
CN (1) CN1013795B (de)
DE (1) DE3865264D1 (de)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004083644A1 (fr) * 2003-03-10 2004-09-30 Thermodyn Groupe compresseur centrifuge
WO2007070595A2 (en) * 2005-12-14 2007-06-21 Eaton Corporation Fuel cell compressor system
WO2010083416A1 (en) 2009-01-16 2010-07-22 Dresser-Rand Company Compact shaft support device for turbomachines
CN102292551A (zh) * 2009-01-23 2011-12-21 诺沃皮尼奥内有限公司 用于喷射和吸取流体旋转机械用的气体的可逆系统
WO2012010514A3 (de) * 2010-07-22 2012-04-12 Siemens Aktiengesellschaft Turboverdichterrotor und turboverdichter
RU2458253C1 (ru) * 2011-03-18 2012-08-10 Закрытое акционерное общество "Научно-исследовательский и конструкторский институт центробежных и роторных компрессоров им. В.Б. Шнеппа" Центробежный компрессорный агрегат
US8430653B2 (en) 2006-02-17 2013-04-30 Nuovo Pignone, S.P.A. Motor compressor
ITFI20130208A1 (it) * 2013-09-05 2015-03-06 Nuovo Pignone Srl "multistage centrifugal compressor"
JP2015143711A (ja) * 2015-04-22 2015-08-06 株式会社日立製作所 振動特性測定装置および振動特性測定方法
EP2956675A4 (de) * 2013-02-13 2016-10-12 Dresser Rand Co Midspan-aktives magnetlager
US9822793B2 (en) 2012-11-06 2017-11-21 Nuovo Pignone Srl Centrifugal compressor with twisted return channel vane
FR3088686A1 (fr) * 2018-11-21 2020-05-22 Thermodyn Motocompresseur a plusieurs sections de compression
EP2295811B1 (de) * 2009-07-10 2022-04-06 Nuovo Pignone Technologie S.r.l. Hochdruckverdichtereinheit für prozessfluide in einer industrieanlage sowie verfahren zum betreiben der anlage

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JPH11294879A (ja) * 1998-02-16 1999-10-29 Daikin Ind Ltd 冷凍装置
EP2533905B1 (de) 2010-02-10 2018-07-04 Dresser-Rand Company Separatorflüssigkeitsbehälter und verfahren dafür
IT1399881B1 (it) * 2010-05-11 2013-05-09 Nuova Pignone S R L Configurazione di tamburo di bilanciamento per rotori di compressore
US9371835B2 (en) 2013-07-19 2016-06-21 Praxair Technology, Inc. Coupling for directly driven compressor
CN103267024B (zh) * 2013-05-15 2015-07-22 北京化工大学 一种带电磁控制器的离心式压缩机
DE112014003121T5 (de) * 2013-07-04 2016-04-07 Ihi Corporation Verdichterlaufrad, Radialverdichter, Bearbeitungsverfahren für ein Verdichterlaufrad und Bearbeitungsvorrichtung für ein Verdichterlaufrad
CN103615405A (zh) * 2013-11-25 2014-03-05 丹东克隆先锋泵业有限公司 双转子磁力驱动多级泵
JP6762724B2 (ja) * 2016-01-22 2020-09-30 三菱重工コンプレッサ株式会社 被動形流体機械の配管
CN106635151A (zh) * 2017-02-15 2017-05-10 沈阳斯特机械制造有限公司 连续重整装置用组合离心压缩机
JP7558083B2 (ja) * 2021-02-25 2024-09-30 三菱重工コンプレッサ株式会社 圧縮機

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CH310025A (de) * 1953-03-19 1955-09-30 Escher Wyss Ag Vielstufiges Axialgebläse.
DE1813335A1 (de) * 1967-12-11 1969-07-24 Gutehoffnungshuette Sterkrade Turboverdichter
GB1166155A (en) * 1966-07-07 1969-10-08 Gutehoffnungshuette Sterkrade Improvements in or relating to Centrifugal Compressors
FR2193427A5 (de) * 1972-07-13 1974-02-15 Bbc Sulzer Turbomaschinen
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DE3527945A1 (de) * 1985-08-03 1987-02-12 Bbc Brown Boveri & Cie Lagerung von rotierenden maschinen

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH310025A (de) * 1953-03-19 1955-09-30 Escher Wyss Ag Vielstufiges Axialgebläse.
GB1166155A (en) * 1966-07-07 1969-10-08 Gutehoffnungshuette Sterkrade Improvements in or relating to Centrifugal Compressors
DE1813335A1 (de) * 1967-12-11 1969-07-24 Gutehoffnungshuette Sterkrade Turboverdichter
FR2193427A5 (de) * 1972-07-13 1974-02-15 Bbc Sulzer Turbomaschinen
DE2542946A1 (de) * 1975-09-26 1977-03-31 Klein Schanzlin & Becker Ag Biegeelastische ausgleichskupplung fuer umwaelzpumpen
EP0087197A1 (de) * 1982-02-22 1983-08-31 BBC Aktiengesellschaft Brown, Boveri & Cie. Antrieb und Lagerung eines Turboverdichters
FR2528127A1 (fr) * 1982-06-04 1983-12-09 Creusot Loire Moto-compresseur centrifuge electrique integre a grande vitesse
DE8337492U1 (de) * 1983-12-28 1985-09-26 BHS-Bayerische Berg-, Hütten- und Salzwerke AG, 8000 München Membrankupplung
DE3527945A1 (de) * 1985-08-03 1987-02-12 Bbc Brown Boveri & Cie Lagerung von rotierenden maschinen

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Cited By (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7144226B2 (en) 2003-03-10 2006-12-05 Thermodyn Centrifugal compressor having a flexible coupling
NO339342B1 (no) * 2003-03-10 2016-11-28 Thermodyn Sentrifugalkompressorenhet
WO2004083644A1 (fr) * 2003-03-10 2004-09-30 Thermodyn Groupe compresseur centrifuge
WO2007070595A2 (en) * 2005-12-14 2007-06-21 Eaton Corporation Fuel cell compressor system
WO2007070595A3 (en) * 2005-12-14 2007-10-11 Eaton Corp Fuel cell compressor system
US7722312B2 (en) 2005-12-14 2010-05-25 Eaton Corporation Fuel cell compressor system
US8430653B2 (en) 2006-02-17 2013-04-30 Nuovo Pignone, S.P.A. Motor compressor
WO2010083416A1 (en) 2009-01-16 2010-07-22 Dresser-Rand Company Compact shaft support device for turbomachines
EP2387654A4 (de) * 2009-01-16 2015-06-03 Dresser Rand Co Kompaktes wellenlager für turbomaschinen
CN102292551B (zh) * 2009-01-23 2014-02-12 诺沃皮尼奥内有限公司 用于喷射和吸取流体旋转机械用的气体的可逆系统
US9151293B2 (en) 2009-01-23 2015-10-06 Nuovo Pignone S.P.A. Reversible system for injecting and extracting gas for fluid rotary machines
CN102292551A (zh) * 2009-01-23 2011-12-21 诺沃皮尼奥内有限公司 用于喷射和吸取流体旋转机械用的气体的可逆系统
EP2295811B1 (de) * 2009-07-10 2022-04-06 Nuovo Pignone Technologie S.r.l. Hochdruckverdichtereinheit für prozessfluide in einer industrieanlage sowie verfahren zum betreiben der anlage
WO2012010514A3 (de) * 2010-07-22 2012-04-12 Siemens Aktiengesellschaft Turboverdichterrotor und turboverdichter
RU2458253C1 (ru) * 2011-03-18 2012-08-10 Закрытое акционерное общество "Научно-исследовательский и конструкторский институт центробежных и роторных компрессоров им. В.Б. Шнеппа" Центробежный компрессорный агрегат
US9822793B2 (en) 2012-11-06 2017-11-21 Nuovo Pignone Srl Centrifugal compressor with twisted return channel vane
EP2956675A4 (de) * 2013-02-13 2016-10-12 Dresser Rand Co Midspan-aktives magnetlager
US9657744B2 (en) 2013-02-13 2017-05-23 Dresser-Rand Company Midspan active magnetic bearing
WO2015032756A1 (en) * 2013-09-05 2015-03-12 Nuovo Pignone Srl Multistage centrifugal compressor
US10711796B2 (en) 2013-09-05 2020-07-14 Nuovo Pignone Srl Multistage centrifugal compressor
ITFI20130208A1 (it) * 2013-09-05 2015-03-06 Nuovo Pignone Srl "multistage centrifugal compressor"
CN111350676B (zh) * 2013-09-05 2022-04-01 诺沃皮尼奥内技术股份有限公司 多级离心压缩机
CN111350676A (zh) * 2013-09-05 2020-06-30 诺沃皮尼奥内股份有限公司 多级离心压缩机
JP2015143711A (ja) * 2015-04-22 2015-08-06 株式会社日立製作所 振動特性測定装置および振動特性測定方法
CN113272558A (zh) * 2018-11-21 2021-08-17 热力学公司 具有多个轴并且具有悬臂式压缩级的压缩机
US20220074418A1 (en) * 2018-11-21 2022-03-10 Thermodyn Sas Motor-driven compressor equipped with multiple compression sections
WO2020104062A1 (en) * 2018-11-21 2020-05-28 Thermodyn Compressor with multiple shafts and with a cantilevered compression stage
FR3088686A1 (fr) * 2018-11-21 2020-05-22 Thermodyn Motocompresseur a plusieurs sections de compression
US11898566B2 (en) 2018-11-21 2024-02-13 Nuovo Pignone Technolgie Srl Motor-driven compressor having a compression section mounted on a free end of a cantilvered shaft
CN113272558B (zh) * 2018-11-21 2024-04-30 热力学公司 具有多个轴并且具有悬臂式压缩级的压缩机

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CN1030816A (zh) 1989-02-01
JPS6429693A (en) 1989-01-31
JPH076518B2 (ja) 1995-01-30
CN1013795B (zh) 1991-09-04
EP0301285B1 (de) 1991-10-02
DE3865264D1 (de) 1991-11-07

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