US3826587A - Centrifugal gas compressor unit - Google Patents

Centrifugal gas compressor unit Download PDF

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Publication number
US3826587A
US3826587A US00349656A US34965673A US3826587A US 3826587 A US3826587 A US 3826587A US 00349656 A US00349656 A US 00349656A US 34965673 A US34965673 A US 34965673A US 3826587 A US3826587 A US 3826587A
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United States
Prior art keywords
housings
gear
compressor
gas
walls
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
US00349656A
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English (en)
Inventor
H Hornschuch
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.)
Ingersoll Rand Co
Original Assignee
Ingersoll Rand Co
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 Ingersoll Rand Co filed Critical Ingersoll Rand Co
Priority to US00349656A priority Critical patent/US3826587A/en
Priority to ZA00740494A priority patent/ZA74494B/xx
Priority to AU64837/74A priority patent/AU474305B2/en
Priority to GB3855575A priority patent/GB1438212A/en
Priority to GB436074A priority patent/GB1438211A/en
Priority to US444739A priority patent/US3861820A/en
Priority to CA193,965A priority patent/CA1016917A/en
Priority to DE2413674A priority patent/DE2413674C2/de
Priority to FR7411538A priority patent/FR2288240A1/fr
Priority to NL7404576.A priority patent/NL157388B/xx
Priority to IT21054/74A priority patent/IT1009729B/it
Priority to JP49040047A priority patent/JPS501409A/ja
Priority to BE143063A priority patent/BE813556A/xx
Application granted granted Critical
Publication of US3826587A publication Critical patent/US3826587A/en
Priority to FR7427611A priority patent/FR2225649B1/fr
Priority to NL7804733A priority patent/NL7804733A/xx
Priority to JP1983093423U priority patent/JPS5943517Y2/ja
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/0018—Shaft assemblies for gearings
    • F16H57/0025—Shaft assemblies for gearings with gearing elements rigidly connected to a shaft, e.g. securing gears or pulleys by specially adapted splines, keys or methods
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/16—Combinations of two or more pumps ; Producing two or more separate gas flows
    • F04D25/163—Combinations of two or more pumps ; Producing two or more separate gas flows driven by a common gearing arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/266—Rotors specially for elastic fluids mounting compressor rotors on 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
    • F04D29/286—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors multi-stage rotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F16D1/08—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key
    • F16D1/0817—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping due to rotation along an eccentric surface, e.g. arcuate wedging elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
    • F16H2057/0235—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly specially adapted to allow easy accessibility and repair
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2700/00—Transmission housings and mounting of transmission components therein; Cooling; Lubrication; Flexible suspensions, e.g. floating frames
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2700/00—Transmission housings and mounting of transmission components therein; Cooling; Lubrication; Flexible suspensions, e.g. floating frames
    • F16H2700/02—Transmissions, specially for working vehicles

Definitions

  • PATENTEDJULSOIBH SHEEY 3 0F 4 CENTRIFUGAL GAS COMPRESSOR UNIT This invention pertains to gas compressors, and in particular to a high speed multi-housing, multi-stage centrifugal gas compressor unit, for high compression ratios, having as its primary application natural gas service such as gathering, pipeline feed, gas injection and gas lift.
  • centrifugal compressors used for natural gas service employ two, or three multi-stage centrifugal compressor units arrangedfin line, driven through a step-up gear, and coupled through high-speed couplings.
  • Such arrangements are very susceptible to vibration, when the alignment becomes distorted.
  • the individual compressor units are vibration-sensitive because of the long shaft overhangs, particularly on the thrust bearing end.
  • Compressor unit maintenance and servicing are time consuming, because the housings or casings of some of the machines, and usually portions of their associated piping, must be completely removed from a baseplate to gain access. So also, the in line arrangement requires a very elongatebaseplate, which is space consuming, and therefore costly, particularly wherein the machinery is mounted on an off-shore platform.
  • a centrifugal gas compressor unit comprising a plurality of separate, elongate, gas compressor housings; a plurality of successive gas compressing stages within each of said housings; means for admitting gas to a first of said housings; means for discharging compressed gas from a last of said housings; means for communicating gas between each of said housings for successive gas compression; said stages each comprising a bladed gas compressor impeller and a vaned diffusor; a shaft confined within each of said, housings, rotatably supporting said impellers; bearing means interposed between each of said shafts and housings for supporting said shafts for rotation; a gear housing, having parallel spaced apart walls, integral with said compressor housings; said compressor housings extending in parallel axes from, and perpendicular to, one of said walls of said gear housing; each of said shafts extending through both of said walls, and having a hollow gear shaft concentrically engaged therewith; each of said gear shafts carries gear means intermediate said walls; an
  • a feature of this invention comprises a multi-housing compressor having a plurality of gas compressing stages in each of parallel housings, the housings being integral with and extending perpendicularly from a gear housing. Rotor assemblies and associated diffusors are slidably replaceable from the respective housings, obviating any requirement to dismantle the gear housings. While the housings each receive gas, sequentially, for further compression, impellers andshafts in a plurality of the compressor housings are of identical weight, with the impellers thereof identical axial length albeit of differing diameters.
  • FIG. 1 is a front, elevational view of an embodiment of the novel centrifugal gas compressor, according to the invention, with the cover plate removed for purposes of clarity;
  • FIG. 2 is a rear elevational view of the embodiment of FIG. 1;
  • FIG. 3 is a fragmentary and half axial illustration of the driving gear within the gear housing
  • FIG. 4 is a fragmentary view of the idler gear within the gear housing
  • FIGS. 5 and 5A are broken, half axial views partly in cross-section, of the second compressor housing. Views 5 and 5A are broken on section lines AA and are to be understood to be substantially symmetrical about the axial centerline thereof;
  • FIG. 6 is an axial illustration of the impeller shaft of the third compressor housing, with but halves of the im pellers thereof shown in cross-sectiomand
  • FIG. 7 is a simple diagrammatic illustration representative of the novel arrangement set forth herein for coupling the impellers to the impeller shafts.
  • the compressor 10 comprises a baseplate 12 which supports a gear housing 14.
  • a plurality of three barrels or compressor housings 16, 18 and 20, are integral with the gear housing, and, extend therefrom, perpendicularly, in parallel axes.
  • the gear housing 14 is defined by an inner wall 22 and an outer wall or cover plate 24.
  • Driving gear 26 (FIG. 1) is in mesh with gear 30 of the first compressor housing 16, and with the idler gear 28.
  • idler gear 28 is in mesh with gears 32 and 32' of the second and third compressor housings 18 and 20, respectively.
  • Driving gear 26 is mounted on a shaft 34 which has a coupling end 36 projecting from the outer wall or cover plate 24, whereat a prime movercan be coupled to impart driving torque to the gear train.
  • the gear housing 14 confines therewithin a reservoir 38, shown in FIGS. 1 and 5.
  • Reservoir 38 has a plurality of outlet ports 40 which receive conduits 42.
  • the conduits 42 are flexible and are conformed to open onto those locations within the gear housing 14 whereat the gears of the gear train mesh.
  • a pair of limbs 44 disposed between the baseplate 12 and gear housing 14 have conduits or passageways (not shown) formed therein, and lubricant discharged by conduits 42 is scavaged therethrough for collection in a sump (not shown) mounted therebelow.
  • the several housings have, inlet and outlet flanged ducts for admitting gas, sequentially to each of the housings in turn.
  • inlet flanged duct 46 admits gas to the first housing 16, this housing having an outlet flanged duct 48.
  • the latter duct by means of piping (not shown) communicates with the inlet 3 flanged duct 46 of the second compressor housing 18, and gas discharged therefrom is passed through its outlet flanged duct' 48' to compressor housing 20.
  • the latter also has both an inlet flanged duct 46 and an outlet flanged duct 48" for discharging the final, totally compressed gas product to a using end item (or to storage).
  • FIGS. 5 and 5A only one compressor housing, specifically the second compressor housing 18, is shown.
  • impeller dummies 64 are carried on the other end of the impeller shaft 50.
  • the dummies 64 are of the same axial length as each of the impellers 52 so that when it is desired to increase or decrease the compressor housing capability it remains only to substitute impellers for one or more of the dummies 64, or vice versa.
  • the rotor assembly comprising the impeller shaft 50, the impellers 52 and the dummies 64, together with the diffusors 54 and housing 56, are slidably removable, as a unit, from the end of housing 18 which is most remote from the gear housing 14, upon removal of retainer 66 whereupon bench dismantling of the unit can follow.
  • Retainer 66 is engaged .with an end seal 68 for securing the removable unit in the housing 18.
  • Retainer 66 in turn, is held within the housing by a split ring 70 and an retaining ring 72. Both rings have surfaces which define a tapered wedge interface.
  • Mounting and tensioning hardware (not shown) secures ring 72 to the retainer 66.
  • a lubricantpassageway 74 is formed within the housing wall or cover plate 24 for admitting lubricant into the reservoir 38, and also for conducting lubricant to shaft bearing 76.
  • reservoir 38 in addition to serving as a lubricant manifold, also serves to suppress the emission of gear-noise from the gear housing 14. As FIGS. 1 and 5 evidence, the reservoir extends fully across the housing 14, and substantially envelops the gear train. In defining a hollow, walled structure, which is substantially closed, it presents a sound buffer intermediate the gear train and the external periphery of the housing 14.
  • the impeller 52 to the impeller shaft 50 without any requirement for keying, bolting, or heating.
  • the nominal inside diameter 82 of the impellers corresponds substantially with the nominal outside diameter 82' of the impeller shaft.
  • the impeller mounting bores as well as the outside diameter of the shaft are formed as something other than true circles. That is, as shown in FIG. 7, a true circular surface it formed about the shaft, and within the impellers, would be represented by the dashed lines and the solid lines contiguous therewith.
  • the impeller bores and the shaft outside diameter or periphery are formed with eccentric surfaces 84 which, therebetween, define three lobes 86.
  • the impellers With the impeller bores and the shaft surface aligned, lobefor-lobe, the impellers are freely, slidably mountable onto the shaft. Then, by forcefully torquing the impellers on the shaft, the priorly aligned lobes separate, rotationally, and effect a binding, circumferentialwedging relationship with" adjacent surfaces 84. It is a teaching of this invention to torque these lobes 86 into such a bound engagement with the adjacent eccentric surfaces 84, as will be greater than any contrary torquing force experienced by the impellers while compressing gas. When necessary to remove an impeller it remains only to reverse the torque lock-up rotation to again slidably align the lobes of both of the impellers and the shaft, whereupon the impellers can be slid off the shaft.
  • the gear train as is evidenced in FIGS. 3, 4, and 5, comprises helical gears which are so oriented as to counter the thrust normally developed by the rotor assembly. Therefore, the thrust bearing 88 (FIG. 5) need not be so large as ordinarily would be necessary. This offers no small economies in machine-space requirements and costs.
  • Housings l8 and 20 contain shafts 50 and 50, respectively (FIGS. 5, 5A, and 6) which are identical in length, weight and configuration. So also, the impellers 52 are identical in weight and axial length AL with impellers 52. This is true, notwithstanding the fact that impellers 52 and 52' have different diameters D and D. This is arranged by having impellers 52 with weighting metal downstream of the blade surface. The common weight and length of these rotor assemblies, and the standard axial length of the impellers, greatly simplifies the fabrication, balancing, and alignment of the compressor unit 10.
  • stages each comprising a bladed gas compressor impeller and a vaned diffusor
  • bearing means interposed between each of said shafts and housings for supporting said shafts for rotation;
  • a gear housing having parallel spaced apart walls, integral with said compressor housings;
  • saidcompressor housings extending in parallel axes from, and perpendicular to one of said walls of said gear housing;
  • each of said shafts extending throughboth of said walls, and having a shallow gear shaft concentrically engaged therewith;
  • each of said gear shafts carries gear means intermediate said walls;
  • a driving gear rotatably supported by and between said walls, drivingly engaged with said idler gear and at least one of said gear means;
  • each of said compressor housings has a plurality of impellers carried on respective ones of said impeller shafts, said impellers and impeller shafts defining rotor assemblies within each of said compressor housings; and t a plurality of said rotor assemblies are of common weight; and wherein I said impellers of oneof said common-weight rotor assemblies have a first diameter, and said impellers of another of said common-weight rotor assemblies have a second diameter, and all impellers of said one and another rotor assemblies are of one, common axial length.
  • a gas compressor according to claim 1, wherein:
  • said driving gear is supported by a stub shaft which is rotatably mounted in said walls;
  • said stub shaft having a portion. which is in penetration of the other of said parallel walls for coupling thereof to a prime mover.
  • a gas compressor according to claim 1, wherein:
  • a gas compressor unit according to claim 1, wherein:
  • each of said impeller shafts is secured in said gear housing by locking means disposed outside of said gear housing.
  • said other of said walls comprises a gear housing cover plate; said cover plate is replaceably secured to said one wall; said cover plate has apertures formed therein; and further including separate covers replaceablysecured over said apertures to provide access to, and to accommodate removal of, said hollow gear shafts through said apertures, upon removal of said separate covers from said cover plate.
  • said gear housing has means therewithin for suppressing sound emission therefrom
  • a centrifugal gas compressor unit comprising:
  • stages each comprising a bladed gas compressor impeller and a vaned diffusor
  • bearing means interposed between each of said shafts and housings for supporting said shafts for rotation;
  • said compressor housings extending in parallel axes from, and perpendicular to one of said walls of said gear housings;
  • each of said shafts extending through both of said walls, and having a hollow.
  • gear shaft concentrically engaged therewith;
  • each of said gear shafts carries gear means intermediate said walls;

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US00349656A 1973-04-10 1973-04-10 Centrifugal gas compressor unit Expired - Lifetime US3826587A (en)

Priority Applications (16)

Application Number Priority Date Filing Date Title
US00349656A US3826587A (en) 1973-04-10 1973-04-10 Centrifugal gas compressor unit
ZA00740494A ZA74494B (en) 1973-04-10 1974-01-23 Centrifugal gas compressor unit
AU64837/74A AU474305B2 (en) 1973-04-10 1974-01-24 Centrifugal gas compressor unit
GB3855575A GB1438212A (en) 1973-04-10 1974-01-30 Method of coupling a compressor impeller shaft to a compressor impeller
GB436074A GB1438211A (en) 1973-04-10 1974-01-30 Centrifugal fas compressor unit
US444739A US3861820A (en) 1973-04-10 1974-02-22 Centrifugal gas compressor unit
CA193,965A CA1016917A (en) 1973-04-10 1974-03-04 Centrifugal gas compressor unit
DE2413674A DE2413674C2 (de) 1973-04-10 1974-03-21 Radialer Turboverdichter
FR7411538A FR2288240A1 (fr) 1973-04-10 1974-03-29 Groupe compresseur centrifuge de gaz
NL7404576.A NL157388B (nl) 1973-04-10 1974-04-03 Centrifugaalcompressorinrichting.
IT21054/74A IT1009729B (it) 1973-04-10 1974-04-08 Gruppo compressore centrifugo di gas
JP49040047A JPS501409A (de) 1973-04-10 1974-04-10
BE143063A BE813556A (fr) 1973-04-10 1974-04-10 Compresseur de gaz centrifuge
FR7427611A FR2225649B1 (de) 1973-04-10 1974-08-08
NL7804733A NL7804733A (nl) 1973-04-10 1978-05-03 Verbinding van de waaier met de waaieras, in het bij- zonder voor een inrichting voor het comprimeren van gassen.
JP1983093423U JPS5943517Y2 (ja) 1973-04-10 1983-06-20 遠心ガス圧縮機ユニツト

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US00349656A US3826587A (en) 1973-04-10 1973-04-10 Centrifugal gas compressor unit

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US44474074A Division 1974-02-22 1974-02-22

Publications (1)

Publication Number Publication Date
US3826587A true US3826587A (en) 1974-07-30

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Family Applications (1)

Application Number Title Priority Date Filing Date
US00349656A Expired - Lifetime US3826587A (en) 1973-04-10 1973-04-10 Centrifugal gas compressor unit

Country Status (11)

Country Link
US (1) US3826587A (de)
JP (2) JPS501409A (de)
AU (1) AU474305B2 (de)
BE (1) BE813556A (de)
CA (1) CA1016917A (de)
DE (1) DE2413674C2 (de)
FR (2) FR2288240A1 (de)
GB (1) GB1438211A (de)
IT (1) IT1009729B (de)
NL (1) NL157388B (de)
ZA (1) ZA74494B (de)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2558463A1 (de) * 1974-12-23 1976-07-01 Ingersoll Rand Co Dichtungs-befestigungsanordnung fuer eine drehdichtung
US4687411A (en) * 1985-03-25 1987-08-18 Ebara Corporation Speed increasing gear for a centrifugal compressor
EP0440902A1 (de) * 1990-02-06 1991-08-14 Deutsche Babcock- Borsig Aktiengesellschaft Getriebe-Turboverdichter
WO1997023731A1 (en) * 1995-12-21 1997-07-03 Comoti-National Research & Design Institute For Turboengines Centrifugal compressor with incorporated gearbox
WO2000032937A1 (en) * 1998-12-03 2000-06-08 American Standard Inc. Impeller to shaft coupling
US20060156728A1 (en) * 2005-01-19 2006-07-20 Michael Rodehau Multistage turbocompressor
US20130315707A1 (en) * 2011-02-02 2013-11-28 Siemens Aktiengesellschaft Stepped parting joint on a transmission housing of a fluid machine
CN103807359A (zh) * 2012-11-15 2014-05-21 上海工程技术大学 宽温度高转速的多头传动器

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Publication number Priority date Publication date Assignee Title
JPS55123254A (en) * 1979-12-17 1980-09-22 Sintokogio Ltd Multiplex signal transmitter-receiver
DE102008031116B4 (de) 2008-05-29 2022-02-03 Man Energy Solutions Se Getriebeturbomaschine für einen Maschinenstrang, Maschinenstrang mit und Getriebe für Getriebeturbomaschine
JP6137983B2 (ja) * 2013-08-02 2017-05-31 株式会社日立製作所 多段遠心圧縮機
CN104653478B (zh) * 2013-11-22 2017-06-30 珠海格力电器股份有限公司 离心式压缩机及离心式冷水机组

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GB626021A (en) * 1938-09-22 1949-07-07 Murray Deodorisers Ltd An improved multi-stage centrifugal pump for cream and like
GB698783A (en) * 1951-12-20 1953-10-21 Inconex Handelsgesellschaft M Compressor apparatus
US2834432A (en) * 1956-04-12 1958-05-13 Thompson Prod Inc Lubrication system
US2840186A (en) * 1954-07-02 1958-06-24 Gen Motors Corp Lubrication system
GB838317A (en) * 1957-07-31 1960-06-22 G & J Weir Ltd Improvements in or relating to centrifugal pumps
US2973894A (en) * 1957-06-17 1961-03-07 Turbo Res Corp Centrifugal compressor for starting jet engines
DE1813335A1 (de) * 1967-12-11 1969-07-24 Gutehoffnungshuette Sterkrade Turboverdichter
US3529698A (en) * 1967-05-05 1970-09-22 Gen Electric Self-operating lubrication system for gear drive units

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DE1750958B1 (de) * 1968-06-21 1971-09-16 Bbc Brown Boveri & Cie Getriebeanordnung zur verteilung der antriebsleistung auf mehrere getriebene wellen

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US1813819A (en) * 1927-04-27 1931-07-07 Gen Electric Gear wheel
US2042496A (en) * 1934-02-19 1936-06-02 Gen Electric Multistage rotary compressor
GB626021A (en) * 1938-09-22 1949-07-07 Murray Deodorisers Ltd An improved multi-stage centrifugal pump for cream and like
GB698783A (en) * 1951-12-20 1953-10-21 Inconex Handelsgesellschaft M Compressor apparatus
US2840186A (en) * 1954-07-02 1958-06-24 Gen Motors Corp Lubrication system
US2834432A (en) * 1956-04-12 1958-05-13 Thompson Prod Inc Lubrication system
US2973894A (en) * 1957-06-17 1961-03-07 Turbo Res Corp Centrifugal compressor for starting jet engines
GB838317A (en) * 1957-07-31 1960-06-22 G & J Weir Ltd Improvements in or relating to centrifugal pumps
US3529698A (en) * 1967-05-05 1970-09-22 Gen Electric Self-operating lubrication system for gear drive units
DE1813335A1 (de) * 1967-12-11 1969-07-24 Gutehoffnungshuette Sterkrade Turboverdichter

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2558463A1 (de) * 1974-12-23 1976-07-01 Ingersoll Rand Co Dichtungs-befestigungsanordnung fuer eine drehdichtung
US4687411A (en) * 1985-03-25 1987-08-18 Ebara Corporation Speed increasing gear for a centrifugal compressor
EP0440902A1 (de) * 1990-02-06 1991-08-14 Deutsche Babcock- Borsig Aktiengesellschaft Getriebe-Turboverdichter
WO1997023731A1 (en) * 1995-12-21 1997-07-03 Comoti-National Research & Design Institute For Turboengines Centrifugal compressor with incorporated gearbox
WO2000032937A1 (en) * 1998-12-03 2000-06-08 American Standard Inc. Impeller to shaft coupling
US20060156728A1 (en) * 2005-01-19 2006-07-20 Michael Rodehau Multistage turbocompressor
US7559200B2 (en) 2005-01-19 2009-07-14 Man Turbo Ag Multistage turbocompressor
CN100516543C (zh) * 2005-01-19 2009-07-22 慕阿恩动力涡轮股份公司 多级涡轮压缩机
US20130315707A1 (en) * 2011-02-02 2013-11-28 Siemens Aktiengesellschaft Stepped parting joint on a transmission housing of a fluid machine
US9631623B2 (en) * 2011-02-02 2017-04-25 Siemens Aktiengesellschaft Stepped parting joint on a transmission housing of a fluid machine
CN103807359A (zh) * 2012-11-15 2014-05-21 上海工程技术大学 宽温度高转速的多头传动器

Also Published As

Publication number Publication date
FR2288240A1 (fr) 1976-05-14
JPS501409A (de) 1975-01-09
FR2225649A1 (de) 1974-11-08
GB1438211A (en) 1976-06-03
NL157388B (nl) 1978-07-17
JPS5934095U (ja) 1984-03-02
CA1016917A (en) 1977-09-06
DE2413674C2 (de) 1984-12-13
FR2288240B1 (de) 1979-07-13
ZA74494B (en) 1975-04-30
FR2225649B1 (de) 1979-03-09
BE813556A (fr) 1974-07-31
DE2413674A1 (de) 1974-11-07
NL7404576A (de) 1974-10-14
AU474305B2 (en) 1976-07-15
JPS5943517Y2 (ja) 1984-12-24
AU6483774A (en) 1975-07-24
IT1009729B (it) 1976-12-20

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