US3733145A - Vand-type centrifugal machine, mainly, high-pressure compressor - Google Patents

Vand-type centrifugal machine, mainly, high-pressure compressor Download PDF

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US3733145A
US3733145A US00120956A US3733145DA US3733145A US 3733145 A US3733145 A US 3733145A US 00120956 A US00120956 A US 00120956A US 3733145D A US3733145D A US 3733145DA US 3733145 A US3733145 A US 3733145A
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seals
cylinder
type centrifugal
space
centrifugal machine
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A Kaplansky
I Korenblit
A Frenkel
A Zakhariev
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    • 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
    • F04D29/08—Sealings
    • F04D29/083—Sealings especially adapted for elastic fluid pumps
    • 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
    • F04D17/125—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 the casing being vertically split
    • 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
    • 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
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/102—Shaft sealings especially adapted for elastic fluid pumps
    • F04D29/104—Shaft sealings especially adapted for elastic fluid pumps the sealing fluid being other than the working fluid or being the working fluid treated
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2230/00—Manufacture
    • F05D2230/60—Assembly methods
    • F05D2230/64—Assembly methods using positioning or alignment devices for aligning or centring, e.g. pins
    • F05D2230/642—Assembly methods using positioning or alignment devices for aligning or centring, e.g. pins using maintaining alignment while permitting differential dilatation
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S277/00—Seal for a joint or juncture
    • Y10S277/927—Seal including fluid pressure differential feature

Definitions

  • a vane type centrifugal machine which is characterized in that rotor bearings and end seals are 11/00 2 jfif g i arranged directly in a set composed of the working compressor stages while, where this set mates with a cylinder encasing the set, seals are mounted for the purpose of hermetically sealing in-the medium being compressed.
  • the present invention relates to turbo-machines and, more particularly, it relates to vane-type centrifugal machines which can be used, for example, in centrifugal compressors or in high-pressure pumps.
  • centrifugal compressors comprising working compressor stages combined in a detachable set, separated from each other by inter-stage seals and encased in a cylinder.
  • the bearings mounting the machine rotor, as well as end seals serving to preclude the leakage of the working fluid from the compressor blading are arranged outside the set.
  • Said known compressors suffer from a number of disadvantages. No provision has been made in them for direct control over gaps in the inter-stage seals. As a result, it is rather difflcult to keep the gaps minimal, which brings about inter-stage leakages of the working fluid and, consequently, a reduced efficiency of the machine. Note should be made that this is especially true of machines featuring relatively great pressure differences between the compressor stages.
  • a principal object of the present invention is to provide a vane-type centrifugal machine featuring minimal gaps in the inter-stage seals and a high operational reliability of bearings and end seals.
  • Said latter seals can comprise a system of annular spaces with sealing members, designed for the delivery and removal of the compressed and sealing media.
  • the top half of the middle portion of the set be of a smaller length than the corresponding bottom half of the set and that, in the gaps formed between the top half of the set and the nondetachable end disks of the set, gauge members be placed.
  • a vane-type centrifugal machine manufactured in accordance with the present invention makes for a successful solution of the problems stated hereinabove.
  • FIG. 1 shows diagrammatically a longitudinal sectional view of the compressor
  • FIG. 2 shows a set of the working compressor stages complete with a detachable top half for control over p
  • FIG. 3 is a connection diagram of seals (units A) shown in FIG. 1;
  • FIG. 4 shows unit B of FIG. 1, on an enlarged scale.
  • the centrifugal compressor described by way of example comprises a cylinder 1 which accommodates bottom and top halves 2 and 3, respectively, of the set of the working compressor stages.
  • the set incorporates a rotor 4, stator blading elements 5 mounted between disks 6 of the set, inter-stage seals 7, bearings 8 of the rotor 4, end seals 9 arranged in non-detachable end disks 10.
  • the set is retained in the cylinder 1 with the aid of a pressure stop ill.
  • gauge members 12 Placed between the top half 3 of the set and the nondetachable disks 10 are gauge members 12, while in places where the set mates with the cylinder 1 there are provided seals (units A) designed for hermetically sealing the medium being compressed.
  • the rotor 4 is arranged on the bottom half 2 of the set on temporary supports with preset gaps along the inter-stage seals 7. Then are installed the non-detachable end disks 10 with the bearings 8 of the rotor 4, end seals 9 and other elements of the stator part of the machine. Following a final check of the gaps along the interstage seals 7, the top half 3 of the set is installed. The assembled set is mounted inthe cylinder l and fixed in place by means of the pressure stop 11.
  • the seal (unit A) comprises annular spaces l3, l4 and 15 (FIG. 3) and sealing members 16.
  • the spaces 13 communicate via channels 17 with the intake annulus of the machine (cavity of minimum gas pressure in the compressor), and via channels 18 with a closed reservoir (not shown) for collecting the leaks of the sealing medium.
  • Supplied to the spaces 14 via channels 19 is a sealing medium under pressure slightly exceeding that in the space 13. This pressure difference is maintained automatically. Possible leaks of the sealing medium are drained to the spaces 15 and removed from the machine via channels 20.
  • the sealing medium supplied to the space 14 is also used for hermetic sealing of the end seals 9 of the rotor 4.
  • each of elements 21 (of, unit B in FIG. 1) serving to bind the disks of the stage featuring the highest pressure of the working fluid there are mounted compensators 22 of the thermal expansion of the set (FIG. 4).
  • a gap a equal to the value of thermal elongation of the set, is left between the surface 23 of the binding element and the bearing surface 24 of the disk of the set.
  • the pressure stop 11 provides a preliminary force sufficient for a reliable retention of the set in the cylinder 1. With a pressure increase in the machine, the gap a is eliminated, and between surfaces 25 and 26 there forms a gap (shown with broken line in FIG. 4) sufficient to compensate for the thermal expansion of the set. Therefore, the thermal elongation of the set is not transmitted to the pressure stop 11.
  • a vane-type centrifugal machine adapted for constituting a high-pressure compressor, said machine comprising: a cylinder, a rotor, inter-stage seals, working compressor stages including blading and combined in a detachable set mating with said cylinder, said stages being separated from each other by said interstage seals and encased in said cylinder; bearings mounting said rotor within said cylider and extending through said stages; end seals on said cylinder to pre clude the leakage of working fluid from said blading; said bearings and said end seals being arranged directly in the set; and further seals to hermetically seal the medium being compressed, said further seals being mounted where said set mates with said cylinder, each said further seal comprising a system of sealing members with annular spaces being provided therebetween and adapted for the supply and removal of compressed and sealing media, said annular spaces including a first annular space communicated with the compressor cavity of minimum gas pressure, a second annular space for the supply of a sealing
  • a vane-type centrifugal machine as claimed in claim 1 comprising means for compensating thermal expansion inside the set.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

A vane-type centrifugal machine is provided which is characterized in that rotor bearings and end seals are arranged directly in a set composed of the working compressor stages while, where this set mates with a cylinder encasing the set, seals are mounted for the purpose of hermetically sealing in the medium being compressed.

Description

United States Patent [191 1111 3,733,145 Kaplansky et al. 1 May 15, 1973 [54] VAND-TYPE CENTRIFUGAL [56] References Cited MACHINE, MAINLY, HIGH-PRESSURE U T STATES PATENTS COMPRESSOR I 1,362,437 12/1920 Robb ..415/134 [75] Inventors: Arkady Fridmanovich Kaplansky; 1,337,873 12/1931 Macmeeken lzya Yakovlevich Korenblit; Andrei 3,235,269 2/1966 Olesen ..277/15 Filippovich Frenkel; Alexandr 3,384,296 5/1968 Kahane ..4l5/l13 Ivanovich Zakhariev, a" of Lenim 3,532,444 10/1970 Strub ..4l5/112 grad, FOREIGN PATENTS OR APPLICATIONS [73] Assignee: Nevsky Mashinostroitelny Zavod 411,913 4/1910 France ..415/199 R imeni V. I. Lenina, Leningrad, 174,673 10/1906 Germany 415/199 R U.S.S.R. 168,058 8/1922 Great Britain ..4l5/l99 R 1 Filed: 4, 1971 Primary Examirier-l-1enry F. Raduazo [21] Appl No 120 956 Attorney-Waters, Roditi, Schwartz & Nissen [57] ABSTRACT [52] US. Cl ..415/l12, 415/199 A, 4lz57lg/ll9s, A vane type centrifugal machine is provided which is characterized in that rotor bearings and end seals are 11/00 2 jfif g i arranged directly in a set composed of the working compressor stages while, where this set mates with a cylinder encasing the set, seals are mounted for the purpose of hermetically sealing in-the medium being compressed.
4 i 3 Claims, 4 Drawing Figures PATENIEDMAY 1 51975 I SHEEI 1 [1F 3 PATENIE MAY 1 51975 SHEET 2 BF 3 PATENTED W1 51% 3.731145 sum 3 OF 3 F/E J VAND-TYPE CENTRIFUGAL MACHINE, MAINLY, HIGH-PRESSURE COMPRESSOR The present invention relates to turbo-machines and, more particularly, it relates to vane-type centrifugal machines which can be used, for example, in centrifugal compressors or in high-pressure pumps.
Presently used for obtaining high-pressure working fluid are centrifugal compressors comprising working compressor stages combined in a detachable set, separated from each other by inter-stage seals and encased in a cylinder. In such known machines, the bearings mounting the machine rotor, as well as end seals serving to preclude the leakage of the working fluid from the compressor blading, are arranged outside the set.
Said known compressors suffer from a number of disadvantages. No provision has been made in them for direct control over gaps in the inter-stage seals. As a result, it is rather difflcult to keep the gaps minimal, which brings about inter-stage leakages of the working fluid and, consequently, a reduced efficiency of the machine. Note should be made that this is especially true of machines featuring relatively great pressure differences between the compressor stages.
In addition, in said known compressors, deformations of the cylinder or-of the end lids, occurring as a result of the internal pressure of the working fluid being compressed, are transmitted to'the rotor bearings and end seals, thus reducing the reliability of operation of these units.
A principal object of the present invention is to provide a vane-type centrifugal machine featuring minimal gaps in the inter-stage seals and a high operational reliability of bearings and end seals.
This is accomplished due to the fact that the bearings mounting the machine rotor and the end seals serving topreclude the leakage of the working fluid from the machine blading are placed inside the set, thereby insuring a direct control of the gaps in the interstage seals and practically eliminating the effect of the cylinder deformation upon the performance of the bearings and end seals. For the purpose of hermetically sealing the medium being compressed, seals are provided at places where the set mates with the cylinder.
Said latter seals can comprise a system of annular spaces with sealing members, designed for the delivery and removal of the compressed and sealing media.
In addition, with a view toward compensating for the thermal expansion of the set, inside the latter on each of the elements serving to bind the disks of the compressor stage featuring the highest pressure of the working fluid, there may be mounted compensators of the thermal expansion of the set.
It is preferred that, with a view to a convenient assembly of the machine, the top half of the middle portion of the set be of a smaller length than the corresponding bottom half of the set and that, in the gaps formed between the top half of the set and the nondetachable end disks of the set, gauge members be placed.
A vane-type centrifugal machine manufactured in accordance with the present invention makes for a successful solution of the problems stated hereinabove.
The present invention will be more apparent upon considering the following detailed description of a preferred embodiment of the invention, due referene being had to the accompanying drawings, in which:
FIG. 1 shows diagrammatically a longitudinal sectional view of the compressor;
FIG. 2 shows a set of the working compressor stages complete with a detachable top half for control over p FIG. 3 is a connection diagram of seals (units A) shown in FIG. 1; and
FIG. 4 shows unit B of FIG. 1, on an enlarged scale.
Referring now to FIGS. 1 and 2 of the drawings, the centrifugal compressor described by way of example comprises a cylinder 1 which accommodates bottom and top halves 2 and 3, respectively, of the set of the working compressor stages. The set incorporates a rotor 4, stator blading elements 5 mounted between disks 6 of the set, inter-stage seals 7, bearings 8 of the rotor 4, end seals 9 arranged in non-detachable end disks 10. The set is retained in the cylinder 1 with the aid of a pressure stop ill.
Placed between the top half 3 of the set and the nondetachable disks 10 are gauge members 12, while in places where the set mates with the cylinder 1 there are provided seals (units A) designed for hermetically sealing the medium being compressed.
During assembly, the rotor 4 is arranged on the bottom half 2 of the set on temporary supports with preset gaps along the inter-stage seals 7. Then are installed the non-detachable end disks 10 with the bearings 8 of the rotor 4, end seals 9 and other elements of the stator part of the machine. Following a final check of the gaps along the interstage seals 7, the top half 3 of the set is installed. The assembled set is mounted inthe cylinder l and fixed in place by means of the pressure stop 11.
The seal (unit A) comprises annular spaces l3, l4 and 15 (FIG. 3) and sealing members 16.
The spaces 13 communicate via channels 17 with the intake annulus of the machine (cavity of minimum gas pressure in the compressor), and via channels 18 with a closed reservoir (not shown) for collecting the leaks of the sealing medium. Supplied to the spaces 14 via channels 19 is a sealing medium under pressure slightly exceeding that in the space 13. This pressure difference is maintained automatically. Possible leaks of the sealing medium are drained to the spaces 15 and removed from the machine via channels 20. The sealing medium supplied to the space 14 is also used for hermetic sealing of the end seals 9 of the rotor 4.
In order to compensate for thermal expansion of the set, on each of elements 21 (of, unit B in FIG. 1) serving to bind the disks of the stage featuring the highest pressure of the working fluid there are mounted compensators 22 of the thermal expansion of the set (FIG. 4).
When assembling the set, a gap a, equal to the value of thermal elongation of the set, is left between the surface 23 of the binding element and the bearing surface 24 of the disk of the set. The pressure stop 11 provides a preliminary force sufficient for a reliable retention of the set in the cylinder 1. With a pressure increase in the machine, the gap a is eliminated, and between surfaces 25 and 26 there forms a gap (shown with broken line in FIG. 4) sufficient to compensate for the thermal expansion of the set. Therefore, the thermal elongation of the set is not transmitted to the pressure stop 11.
What is claimed is:
l. A vane-type centrifugal machine adapted for constituting a high-pressure compressor, said machine comprising: a cylinder, a rotor, inter-stage seals, working compressor stages including blading and combined in a detachable set mating with said cylinder, said stages being separated from each other by said interstage seals and encased in said cylinder; bearings mounting said rotor within said cylider and extending through said stages; end seals on said cylinder to pre clude the leakage of working fluid from said blading; said bearings and said end seals being arranged directly in the set; and further seals to hermetically seal the medium being compressed, said further seals being mounted where said set mates with said cylinder, each said further seal comprising a system of sealing members with annular spaces being provided therebetween and adapted for the supply and removal of compressed and sealing media, said annular spaces including a first annular space communicated with the compressor cavity of minimum gas pressure, a second annular space for the supply of a sealing medium and a third annular space for the drainage of the sealing medium, the second space being located between the first and third spaces and the mediums in the second space being at higher pressure than that in the first space.
2. A vane-type centrifugal machine as claimed in claim 1 comprising means for compensating thermal expansion inside the set.
3. A vane-type centrifugal machine as claimed in claim 1, wherein said set includes top and bottom halves and the top half of the middle portion of the set is of a smaller length than the corresponding bottom half of the set whereby there are formed gaps, compris ing gauge members in the gaps.

Claims (3)

1. A vane-type centrifugal machine adapted for constituting a high-pressure compressor, said machine comprising: a cylinder, a rotor, inter-stage Seals, working compressor stages including blading and combined in a detachable set mating with said cylinder, said stages being separated from each other by said inter-stage seals and encased in said cylinder; bearings mounting said rotor within said cylider and extending through said stages; end seals on said cylinder to preclude the leakage of working fluid from said blading; said bearings and said end seals being arranged directly in the set; and further seals to hermetically seal the medium being compressed, said further seals being mounted where said set mates with said cylinder, each said further seal comprising a system of sealing members with annular spaces being provided therebetween and adapted for the supply and removal of compressed and sealing media, said annular spaces including a first annular space communicated with the compressor cavity of minimum gas pressure, a second annular space for the supply of a sealing medium and a third annular space for the drainage of the sealing medium, the second space being located between the first and third spaces and the mediums in the second space being at higher pressure than that in the first space.
2. A vane-type centrifugal machine as claimed in claim 1 comprising means for compensating thermal expansion inside the set.
3. A vane-type centrifugal machine as claimed in claim 1, wherein said set includes top and bottom halves and the top half of the middle portion of the set is of a smaller length than the corresponding bottom half of the set whereby there are formed gaps, comprising gauge members in the gaps.
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Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3942908A (en) * 1974-05-03 1976-03-09 Norwalk-Turbo, Inc. Gas turbine driven high speed centrifugal compressor unit
US4057371A (en) * 1974-05-03 1977-11-08 Norwalk-Turbo Inc. Gas turbine driven high speed centrifugal compressor unit
US4087200A (en) * 1974-12-05 1978-05-02 Izya Yakovlevich Korenblit Stator of multistage centrifugal compressor
US4128248A (en) * 1976-06-04 1978-12-05 Leybold-Heraeus Gmbh & Co. Kg Shaft seal
US4218181A (en) * 1977-11-21 1980-08-19 Hitachi, Ltd. Barrel type centrifugal turbo-machine
US4518311A (en) * 1979-10-03 1985-05-21 Klein, Schanzlin & Becker Aktiengesellschaft Centrifugal pump
US4536128A (en) * 1982-08-31 1985-08-20 Klein, Schanzlin & Becker Aktiengesellschaft Barrel housing for centrifugal fluid machines
US4753571A (en) * 1985-11-06 1988-06-28 Klein, Schanzlin & Becker Aktiengesellschaft Liquefied gas pump
US4756665A (en) * 1986-02-03 1988-07-12 Mitsubishi Jukogyo Kabushiki Kaisha Centrifugal compressor
EP1369594A3 (en) * 2002-06-05 2004-08-25 Nuovo Pignone Holding S.P.A. Sealing system for centrifugal compressors
WO2011032549A1 (en) * 2009-09-21 2011-03-24 Man Diesel & Turbo Se Axial-radial turbomachine
US20110318163A1 (en) * 2010-06-23 2011-12-29 Hitachi Plant Technologies, Ltd. Barrel-shaped centrifugal compressor
US20120156023A1 (en) * 2009-07-31 2012-06-21 Man Diesel & Turbo Se Radial Compressor And Method For Producing A Radial Compressor
EP3236082A4 (en) * 2015-01-27 2018-01-03 Mitsubishi Heavy Industries Compressor Corporation Centrifugal compressor bundle and centrifugal compressor
EP2679825A4 (en) * 2011-02-25 2018-01-17 Mitsubishi Heavy Industries Compressor Corporation Compressor
US11788546B2 (en) * 2019-11-01 2023-10-17 Mitsubishi Heavy Industries Compressor Corporation Ammonia plant synthesis gas compressor train

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE174673C (en) *
FR411913A (en) * 1910-01-24 1910-06-29 Paul Mortier Recessed guide diaphragm for centrifugal pumps and multistage turbochargers
US1362437A (en) * 1920-04-14 1920-12-14 Gen Electric Elastic-fluid turbine
GB168058A (en) * 1920-08-20 1922-08-03 Acec Improvements in and relating to centrifugal pumps, compressors and ventilating fans
US1837873A (en) * 1928-01-25 1931-12-22 Worthington Pump & Mach Corp Centrifugal pump
US3235269A (en) * 1962-09-05 1966-02-15 Stal Laval Turbin Ab Method of sealing a turbine or compressor shaft
US3384296A (en) * 1967-05-19 1968-05-21 Kahane Wilhelm Sealing of horizontally-split centrifugal compressors
US3532444A (en) * 1967-08-18 1970-10-06 Sulzer Ag Gas pumping apparatus

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE174673C (en) *
FR411913A (en) * 1910-01-24 1910-06-29 Paul Mortier Recessed guide diaphragm for centrifugal pumps and multistage turbochargers
US1362437A (en) * 1920-04-14 1920-12-14 Gen Electric Elastic-fluid turbine
GB168058A (en) * 1920-08-20 1922-08-03 Acec Improvements in and relating to centrifugal pumps, compressors and ventilating fans
US1837873A (en) * 1928-01-25 1931-12-22 Worthington Pump & Mach Corp Centrifugal pump
US3235269A (en) * 1962-09-05 1966-02-15 Stal Laval Turbin Ab Method of sealing a turbine or compressor shaft
US3384296A (en) * 1967-05-19 1968-05-21 Kahane Wilhelm Sealing of horizontally-split centrifugal compressors
US3532444A (en) * 1967-08-18 1970-10-06 Sulzer Ag Gas pumping apparatus

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3942908A (en) * 1974-05-03 1976-03-09 Norwalk-Turbo, Inc. Gas turbine driven high speed centrifugal compressor unit
US4057371A (en) * 1974-05-03 1977-11-08 Norwalk-Turbo Inc. Gas turbine driven high speed centrifugal compressor unit
US4087200A (en) * 1974-12-05 1978-05-02 Izya Yakovlevich Korenblit Stator of multistage centrifugal compressor
US4128248A (en) * 1976-06-04 1978-12-05 Leybold-Heraeus Gmbh & Co. Kg Shaft seal
US4218181A (en) * 1977-11-21 1980-08-19 Hitachi, Ltd. Barrel type centrifugal turbo-machine
US4518311A (en) * 1979-10-03 1985-05-21 Klein, Schanzlin & Becker Aktiengesellschaft Centrifugal pump
US4536128A (en) * 1982-08-31 1985-08-20 Klein, Schanzlin & Becker Aktiengesellschaft Barrel housing for centrifugal fluid machines
US4753571A (en) * 1985-11-06 1988-06-28 Klein, Schanzlin & Becker Aktiengesellschaft Liquefied gas pump
US4756665A (en) * 1986-02-03 1988-07-12 Mitsubishi Jukogyo Kabushiki Kaisha Centrifugal compressor
EP1369594A3 (en) * 2002-06-05 2004-08-25 Nuovo Pignone Holding S.P.A. Sealing system for centrifugal compressors
US20120156023A1 (en) * 2009-07-31 2012-06-21 Man Diesel & Turbo Se Radial Compressor And Method For Producing A Radial Compressor
US9488189B2 (en) * 2009-07-31 2016-11-08 Man Diesel & Turbo Se Radial compressor and method for producing a radial compressor
WO2011032549A1 (en) * 2009-09-21 2011-03-24 Man Diesel & Turbo Se Axial-radial turbomachine
US20110318163A1 (en) * 2010-06-23 2011-12-29 Hitachi Plant Technologies, Ltd. Barrel-shaped centrifugal compressor
US9004857B2 (en) * 2010-06-23 2015-04-14 Hitachi, Ltd. Barrel-shaped centrifugal compressor
EP2679825A4 (en) * 2011-02-25 2018-01-17 Mitsubishi Heavy Industries Compressor Corporation Compressor
EP3236082A4 (en) * 2015-01-27 2018-01-03 Mitsubishi Heavy Industries Compressor Corporation Centrifugal compressor bundle and centrifugal compressor
US10683872B2 (en) 2015-01-27 2020-06-16 Mitsubishi Heavy Industries Compressor Corporation Centrifugal compressor bundle and centrifugal compressor
US11788546B2 (en) * 2019-11-01 2023-10-17 Mitsubishi Heavy Industries Compressor Corporation Ammonia plant synthesis gas compressor train

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