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EP0301285B1 - Compresseur centrifuge - Google Patents

Compresseur centrifuge Download PDF

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Publication number
EP0301285B1
EP0301285B1 EP88110809A EP88110809A EP0301285B1 EP 0301285 B1 EP0301285 B1 EP 0301285B1 EP 88110809 A EP88110809 A EP 88110809A EP 88110809 A EP88110809 A EP 88110809A EP 0301285 B1 EP0301285 B1 EP 0301285B1
Authority
EP
European Patent Office
Prior art keywords
axles
gas
casing
axle
compressor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP88110809A
Other languages
German (de)
English (en)
Other versions
EP0301285A1 (fr
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/fr
Application granted granted Critical
Publication of EP0301285B1 publication Critical patent/EP0301285B1/fr
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 accomodated 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.
  • DE-A-18 13 335 discloses 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, coupling means for coupling said axles with one another as arrayed in series sequentially in such order that said gas can be compressed towards one side, a casing' for supporting said plurality of coupled axis having a gas suction port at one end and a gas delivery port at the other end, and a sealing means at the drive side of said plurality of axles.
  • Such a compressor comprises a casing housing first and second aligned shafts each bearing a plurality of centrifugal impellers to increasingly compress gas from stage to stage.
  • Said gas is introduced into the compressor at the low pressure side thereof through a radial suction opening, fed through the several stages of the compressor increasingly pressurized thereby and is delivered as a high pressure gas through a radial outlet port at the gas delivery side of the compressor.
  • the gas flow passes through external cooling means bridging adjacent stages, respectively.
  • the adjacent axial ends of both shafts are coupled through a planatory gear transmission.
  • Said multi stage centrifugal compressor including at least two compressor units housed in a common casing, however, suffers from the following drawbacks:
  • Fig. 3 illustrates another 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.
  • the 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 manner 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 as described above, wherein said casing comprises electro magnetic bearings for radially supporting said plurality of axles integrally at their respective opposite ends, the casing defines said gas suction port to extend axially through a front wall of the casing, and said coupling means are adapted to allow misalignment of said axles.
  • the centrifugal compressor according to the invention offers the following advantages over the prior art compressor.
  • the coupling means according to the present invention inter-linking the respective axles are designed to allow a certain misalignment of the axles, i.e. a radial deviation of each of the axles from a notional common center axis of the plurality of axles.
  • the compressor according to the present invention provides an axial suction opening to enable a large volume of gas to be sucked into the compressor with minimal flow resistance loss.
  • each of the axles is supported through contact free electric magnetic bearings resulting in minimal friction loss and wear and, moreover, avoiding lubricating oil to be necssary and, consequently, avoiding the sealing problems to occur between pressurized gas and lubricating oil inside the compressor;
  • the compressor according to the present invention requires only one gas sealing means to be provided in between an axle and the casing so that manufacturing and maintenance of the compressor becomes easy.
  • 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)

Claims (11)

  1. Un compresseur centrifuge comportant une pluralité d'axes ayant chacun des roues centrifuges qui peuvent comprimer le gaz en utilisant la force centrifuge exercée sur le gaz, des moyens de couplage pour coupler lesdits axes l'un avec l'autre, ces axes étant alignés séquentiellement en série de telle manière que ledit gaz puisse être comprimé vers un côté, une enveloppe pour supporter ladite pluralité d'axes couplés et présentant un orifice d'aspiration de gaz à une extrémité et un orifice de refoulement de gaz à l'autre extrémité, et des moyens de fermeture étanche du côté entraînement de ladite pluralité d'axes, caractérisé en ce que ladite enveloppe (1) comporte des paliers électro-magnétiques (13,14,15,16, 17,18) pour supporter radialement ladite pluralité d'axes (3,7,12) comme un ensemble unique à leurs extrémités opposées respectives, l'enveloppe (1) définit ledit orifice (2) d'aspiration de gaz pour qu'il s'étende axialement à travers une paroi avant de ladite enveloppe (1), et lesdits moyens de couplage (19) sont agencés pour permettre un défaut d'alignement desdits axes (3,7,12).
  2. Un compresseur centrifuge tel que revendiqué dans la revendication 1, caractérisé en ce qu'une partie (4) de refroidissement du gaz pour refroidir le gaz comprimé par les roues centrifuges sur les axes (3,7,12) est montée sur ladite enveloppe.
  3. Un compresseur centrifuge tel que revendiqué dans les revendications 1 ou 2, caractérisé en ce que lesdits moyens de couplage (19) sont agencés pour empêcher un déplacement relatif des axes couplés (3,7,12) pour les rapprocher l'un de l'autre en direction axiale.
  4. Un compresseur centrifuge tel que revendiqué dans la revendication 3, caractérisé en ce que lesdits moyens de couplage (19) sont constitués d'arbres de retenue (36, 37) montés sur les extrémités axiales adjacentes des axes associés (3,7,12) pour être en face l'un de l'autre, deux disques souples (32) disposés autour desdits arbres de retenue (36,37) et montés respectivement sur les axes respectifs (3,7,12), et un tube (33) de transmission de couple relié auxdits disques souples (32).
  5. Un compresseur centrifuge tel que revendiqué dans la revendication 4, caractérisé en ce que l'un au moins des arbres de retenue (36,37) présente une saillie (39) au centre de sa surface extrême axiale, agencée pour empêcher un rapprochement axial des arbres de retenue (36,37) l'un vers l'autre.
  6. Un compresseur centrifuge tel que revendiqué dans l'une au moins des revendications précédentes 1 à 5, caractérisé en ce que lesdits moyens de fermeture étanche comportent un dispositif de fermeture étanche au gaz disposé seulement à l'emplacement où l'un (12) de la pluralité des axes (3,7,12) pénètre dans une plaque extrême (22) de l'enveloppe (1) pour recevoir le couple à partir d'un couplage d'entraînement (20) pour transmettre ledit couple aux autres axes (3,7,12) de ladite pluralité d'axes (3,7,12).
  7. Un compresseur centrifuge tel que revendiqué dans l'une au moins des revendications précédentes 1 à 6, caractérisé en ce qu'un disque (25) d'équilibrage de pression est disposé sur l'axe respectif (12) du côté aval de la roue de l'étage final de manière à fournir une réduction de pression du gaz sortant à haute pression fuyant depuis ledit étage vers une chambre (24) d'équilibrage de pression à travers des ailettes de labyrinthe pour équilibrer de manière appropriée entre elles les forces gazeuses agissant en direction axiale sur ledit axe (12).
  8. Un compresseur centrifuge tel que revendiqué dans la revendication 7, caractérisé en ce que ladite chambre (24) d'équilibrage de pression communique avec un environnement à basse pression dans la zone de l'orifice d'aspiration de gaz (2) à travers un tube (21) d'équilibrage de pression prévu sur une plaque extrême (22) de l'enveloppe (1).
  9. Un compresseur centrifuge tel que revendiqué dans l'une au moins des revendications précédentes 1 à 8, caractérisé en ce qu'un palier de poussée électro-magnétique (29) est prévu pour supporter une extrémité d'un axe associé (12) de l'étage final à haute pression de la pluralité d'axes (3,7,12) pour appliquer une force de poussée dirigée axialement vers l'intérieur à ladite pluralité d'axes (3,7,12) à partir du côté refoulement du gaz du compresseur, tandis qu'un palier à force de traction magnétique est associé au premier axe associé à basse pression (3) de la pluralité d'axes (3,7,12) pour appliquer une force de traction opposée dirigée axialement vers l'intérieur à ladite pluralité d'axes (3,7,12) à partir du côté aspiration de gaz du compresseur.
  10. Un compresseur centrifuge tel que revendiqué dans la revendication 9, caractérisé en ce que ledit palier de poussée électro-magnétique (29) est fixé à l'enveloppe (1) et conçu pour être situé de part et d'autre d'une collerette de poussée (28) fixée audit axe (12), pour permettre ainsi à la position de l'axe (12) d'être détectée à travers le palier de poussée (29) par l'intermédiaire d'un dispositif extérieur de commande, de manière à ramener l'axe (12) à une position prédéterminée.
  11. Un compresseur centrifuge tel que revendiqué dans la revendication 8, caractérisé en ce que ledit palier (27) de force de traction magnétique est prévu en conjonction avec la surface arrière d'une roue (26) qui produit des effets initiaux d'aspiration de gaz pour appliquer à ladite roue (26) une force axiale de traction.
EP88110809A 1987-07-23 1988-07-06 Compresseur centrifuge Expired - Lifetime EP0301285B1 (fr)

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 EP0301285A1 (fr) 1989-02-01
EP0301285B1 true EP0301285B1 (fr) 1991-10-02

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP88110809A Expired - Lifetime EP0301285B1 (fr) 1987-07-23 1988-07-06 Compresseur centrifuge

Country Status (4)

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

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US9371835B2 (en) 2013-07-19 2016-06-21 Praxair Technology, Inc. Coupling for directly driven compressor
EP3884167B1 (fr) * 2018-11-21 2024-01-10 Thermodyn SAS Compresseur avec une pluralité d'arbres et avec un étage de compression en porte-à-faux

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RU2333398C2 (ru) * 2003-03-10 2008-09-10 Термодин Центробежный компрессорный агрегат
DE102005052077B4 (de) * 2005-10-28 2016-11-24 Man Diesel & Turbo Se Vorrichtung zur seitlichen Montage und Demontage eines Kompressorbarrels
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IT1399171B1 (it) * 2009-07-10 2013-04-11 Nuovo Pignone Spa Unita' di compressione ad alta pressione per fluidi di processo di impianti industriali e relativo metodo di funzionamento
IT1399881B1 (it) * 2010-05-11 2013-05-09 Nuova Pignone S R L Configurazione di tamburo di bilanciamento per rotori di compressore
DE102010031942A1 (de) * 2010-07-22 2012-01-26 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
ITCO20120055A1 (it) 2012-11-06 2014-05-07 Nuovo Pignone Srl Pala di canale di ritorno per compressori centrifughi
US9657744B2 (en) 2013-02-13 2017-05-23 Dresser-Rand Company Midspan active magnetic bearing
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
JPWO2015002066A1 (ja) * 2013-07-04 2017-02-23 株式会社Ihi コンプレッサインペラ、遠心圧縮機、コンプレッサインペラの加工方法、および、コンプレッサインペラの加工装置
ITFI20130208A1 (it) * 2013-09-05 2015-03-06 Nuovo Pignone Srl "multistage centrifugal compressor"
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
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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
CN113676014B (zh) * 2021-07-27 2025-10-03 鑫磊压缩机股份有限公司 一种通过磁性联轴器连接磁悬浮电机驱动的mcl压缩系统

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DE2542946A1 (de) * 1975-09-26 1977-03-31 Klein Schanzlin & Becker Ag Biegeelastische ausgleichskupplung fuer umwaelzpumpen
CH663644A5 (de) * 1982-02-22 1987-12-31 Bbc Brown Boveri & Cie Turboverdichter.
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
JP3825134B2 (ja) 1997-04-18 2006-09-20 株式会社リコー 画像補正装置及び画像補正方法

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9095856B2 (en) 2010-02-10 2015-08-04 Dresser-Rand Company Separator fluid collector and method
US9371835B2 (en) 2013-07-19 2016-06-21 Praxair Technology, Inc. Coupling for directly driven compressor
EP3884167B1 (fr) * 2018-11-21 2024-01-10 Thermodyn SAS Compresseur avec une pluralité d'arbres et avec un étage de compression en porte-à-faux

Also Published As

Publication number Publication date
CN1030816A (zh) 1989-02-01
DE3865264D1 (de) 1991-11-07
CN1013795B (zh) 1991-09-04
JPH076518B2 (ja) 1995-01-30
EP0301285A1 (fr) 1989-02-01
JPS6429693A (en) 1989-01-31

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