WO1997028372A1 - Compresseurs - Google Patents

Compresseurs Download PDF

Info

Publication number
WO1997028372A1
WO1997028372A1 PCT/GB1997/000292 GB9700292W WO9728372A1 WO 1997028372 A1 WO1997028372 A1 WO 1997028372A1 GB 9700292 W GB9700292 W GB 9700292W WO 9728372 A1 WO9728372 A1 WO 9728372A1
Authority
WO
WIPO (PCT)
Prior art keywords
compressor
shaft
impeller
hollow
stages
Prior art date
Application number
PCT/GB1997/000292
Other languages
English (en)
Inventor
Richard Julius Gozdawa
Original Assignee
Compact Radial Compressors 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 Compact Radial Compressors Ltd. filed Critical Compact Radial Compressors Ltd.
Priority to DE69708850T priority Critical patent/DE69708850T2/de
Priority to AT97902446T priority patent/ATE210246T1/de
Priority to EP97902446A priority patent/EP0883749B1/fr
Priority to AU16091/97A priority patent/AU1609197A/en
Publication of WO1997028372A1 publication Critical patent/WO1997028372A1/fr

Links

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
    • F04D29/0566—Ceramic bearing designs
    • 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
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D25/0606—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump
    • 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
    • F04D29/057—Bearings hydrostatic; hydrodynamic
    • 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

Definitions

  • This invention relates to compressors.
  • it relates to a compressor which provides a supply of compressed air or other working gas which is free of oil or other bearing lubricating material.
  • This type of compressor is desirable when a source of compressed air is used to process food, pharmaceutical or other sensitive material which must not be contaminated by any substance borne with the gas.
  • Attempts to design oil free compressors in the past have met with varying degrees of success but a problem still remains in achieving good cooling of the compressor mechanism, particularly with high speed rotary type compressors.
  • the present invention arose in an attempt to provide an improved oil-free air or gas compressor of the rotary type.
  • a compressor comprising a rotatable shaft, drive means for rotating the shaft and one or more impeller rotor stages mounted on the shaft, wherein the rotatable shaft and rotor stages are hollow and means are provided to allow a coolant fluid to flow axially through them to cool the motor and compressor if needed in operation.
  • a method of cooling the rotor of compressor having a rotatable shaft, drive means for rotating the shaft and one or more impeller rotor stages mounted on the shaft comprises the shaft and impeller stages being hollow, the method comprising causing a coolant fluid to flow axially through the shaft and impeller stages to cool rotor and the impeller in operation if required.
  • the coolant fluid may be water or any other suitable liquid or fluid material.
  • An embodiment of the invention will now be described, by way of example only, with reference to the accompanying drawing which shows schematically a compressor.
  • the compressor shown in the figure is a two- stage turbo-compressor but may of course have more stages than this. It is usual to have two or more stages in a compressor of this type.
  • the compressor is driven directly by a high speed DC motor, shown as stator 1 and rotor 10, which may be arranged to drive at a speed of, say, 50,000-100,000 rpm, although this figure may vary depending on the use required of the compressor.
  • the motor is controlled by an invertor (not shown) to run directly at the speed required by the compressor and thereby avoid the necessity for a speed- increasing gear box and its associated lubrication system.
  • the motor is used to rotate the rotor 10 in conventional manner.
  • the shaft carries permanent magnets 10a which are acted upon by the stator windings. This is connected to two turbo-compressor stages 2 and 3, the motor being positioned between the two compressor stages.
  • Journal bearings 4, 5 are provided which support the shaft radially.
  • the journal bearings will typically be hydrostatic, gas pressurised, ones with the process air or gas as the supporting medium. Since any compressor takes a finite time to start up the bearings are initially supplied with air or gas from a small accumulator 8 but once the compressor is up to speed then the supply is taken direct from the compressor. Many types of bearing may be used successfully with this arrangement.
  • the design of the compressor stages 2, 3 is preferably such that any axial thrust is minimised, it will generally be found necessary to include a thrust bearing in the system. In the embodiment shown, this is in the form of a spiral groove thrust bearing 6, 7 which is used to carry any residual axial load. This spiral groove bearing also preferably operates using the process air or gas of the system.
  • the shaft assembly itself comprises four main hollow components.
  • a central rotor portion 10 lies wholly within the motor stator 1 and carries the permanent magnets 10a as described above. At each end of this central portion is a respective one of two end pieces 9, 11 which provide the bearing journals 4, 5 and also the thrust collar 6a for the thrust bearings 6, 7.
  • the bearings are mounted outboard of the motor and inboard of the impellers, the thrust bearing being on the portion between the motor and the second impeller stage 3.
  • Each of the outer portions is spigotted to the centre portion and respective impellers 15 and 16 are located by spigots onto the outer portions 9 and 11.
  • an in-line system results in which central portion 10, outer portions 9, 11 and impellers 15 and 16 all rotate together under the action of motor 1.
  • the assembly is clamped together by means of a hollow tie bolt 12 running axially through their common hollow centres.
  • the tie bolt is hollow to allow for cooling water to be passed through it, and thereby through the centre of the shaft, impeller assembly during operation. Heat is inevitably generated in the rotor due to eddy current losses in the magnet, particularly at high speed motor operation and the use of coolant water through the central axis of the shaft-impeller assembly provides an effective way of cooling the system.
  • the water is fed in at a non-rotating input 22 which feeds directly into the (rotating) tie bolt 12.
  • two respective chambers 13, 14 are provided, one at the eye of each impeller 15, 16. Each has is own labyrinth seal.
  • each of the stages in the described embodiment comprises a backward sloping impeller 15, 16 followed by a vaned or vaneless diffuser or a pipe diffuser 17, 18 and this is sized to give maximum static pressure recovery before delivery the air into a low loss scroll 19, 20.
  • the design of impellers, diffusers and scrolls is of course well known.
  • the air or gas to be processed is arranged to enter the first compressor stage at a direction perpendicular to the machine's axis through a row of variable inlet guide vanes 21.
  • This feature of the gas entering from a direction other than in-line and with variable guide vanes offers a considerable degree of flow control which is not possible with positive displacement type machines.
  • the air or gas is then acted upon by the impeller 15 and leaves this stage at portion 2a in the figure to enter an intercooler (not shown) . Intercoolers themselves are well known and the intercooler has not been shown for clarity.
  • the air or gas then passes through the intercooler before entering the second impeller stage at 3a. The process ensures a low power consumption and reduces the degree of after cooling which may be required in some applications.
  • the air or gas is enacted upon by the second impeller 16 and allowed the exit the system in its processed form.
  • the rotor mechanism (rotors, shaft, etc) is entirely or partially of ceramic. This helps to achieve thermal stability and lightness in the machine.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Chemical & Material Sciences (AREA)
  • Ceramic Engineering (AREA)
  • Fluid Mechanics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Compressor (AREA)
  • Separation By Low-Temperature Treatments (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

Compresseur comportant un arbre rotatif (10), des moyens de commande (1) servant à faire tourner l'arbre et un ou plusieurs étages de rotor (15, 16) montés sur l'arbre. Cet arbre rotatif (10) et les étages de rotor (15, 16) sont creux et des moyens (22, 23, 12) permettent à un liquide réfrigérant de s'écouler axialement à travers lesdits moyens, afin de refroidir le rotor et le compresseur, si nécessaire, lorsqu'ils sont en fonction. Un tirant creux (12) est monté à travers l'arbre et les rotors, et le réfrigérant (par exemple, de l'eau) est mis en circulation à travers le tirant.
PCT/GB1997/000292 1996-02-02 1997-01-31 Compresseurs WO1997028372A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
DE69708850T DE69708850T2 (de) 1996-02-02 1997-01-31 Kompressor
AT97902446T ATE210246T1 (de) 1996-02-02 1997-01-31 Kompressor
EP97902446A EP0883749B1 (fr) 1996-02-02 1997-01-31 Compresseur
AU16091/97A AU1609197A (en) 1996-02-02 1997-01-31 Compressors

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB9602126.6 1996-02-02
GBGB9602126.6A GB9602126D0 (en) 1996-02-02 1996-02-02 Compressors

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US09/128,377 Continuation-In-Part US6296441B1 (en) 1997-08-05 1998-08-03 Compressors

Publications (1)

Publication Number Publication Date
WO1997028372A1 true WO1997028372A1 (fr) 1997-08-07

Family

ID=10788015

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB1997/000292 WO1997028372A1 (fr) 1996-02-02 1997-01-31 Compresseurs

Country Status (6)

Country Link
EP (1) EP0883749B1 (fr)
AT (1) ATE210246T1 (fr)
AU (1) AU1609197A (fr)
DE (1) DE69708850T2 (fr)
GB (1) GB9602126D0 (fr)
WO (1) WO1997028372A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0896158A2 (fr) * 1997-08-05 1999-02-10 Corac Group plc Compresseurs
BE1012157A3 (fr) * 1997-03-19 2000-06-06 Hitachi Ltd Compresseur centrifuge a deux etages.
EP1321680A3 (fr) * 2001-12-22 2003-12-10 Miscel Oy Turbomachine
DE19917958B4 (de) * 1999-04-21 2014-03-06 Institut für Luft- und Kältetechnik gemeinnützige Gesellschaft mbH Kühleinrichtung für Elektromotoren
CN105782075A (zh) * 2015-01-13 2016-07-20 Lg电子株式会社 涡轮压缩机以及制冷机

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009054773A1 (de) * 2009-12-16 2011-06-22 Piller Industrieventilatoren GmbH, 37186 Turboverdichter und Verdichteranlage umfassend einen derartigen Turboverdichter
US9839428B2 (en) 2013-12-23 2017-12-12 Ethicon Llc Surgical cutting and stapling instruments with independent jaw control features
US10166026B2 (en) 2015-08-26 2019-01-01 Ethicon Llc Staple cartridge assembly including features for controlling the rotation of staples when being ejected therefrom

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2888193A (en) * 1957-02-14 1959-05-26 Garrett Corp Motor driven compressor
FR1352260A (fr) * 1963-01-04 1964-02-14 Aspirateur
US3133693A (en) * 1962-05-17 1964-05-19 Gen Electric Sump seal system
EP0402095A2 (fr) * 1989-06-06 1990-12-12 Ngk Insulators, Ltd. Rotor céramique pour turbocompresseur à suralimentation
WO1995024563A1 (fr) * 1994-03-08 1995-09-14 Welsh Innovations Limited Compresseur

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2888193A (en) * 1957-02-14 1959-05-26 Garrett Corp Motor driven compressor
US3133693A (en) * 1962-05-17 1964-05-19 Gen Electric Sump seal system
FR1352260A (fr) * 1963-01-04 1964-02-14 Aspirateur
EP0402095A2 (fr) * 1989-06-06 1990-12-12 Ngk Insulators, Ltd. Rotor céramique pour turbocompresseur à suralimentation
WO1995024563A1 (fr) * 1994-03-08 1995-09-14 Welsh Innovations Limited Compresseur

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
"ANWENDUNG DER GASDYNAMISCHEN LAGER IM THERMISCHEN TURBOMASCHINENBAU", BROWN BOVERI MITTEILUNGEN, vol. 51, no. 12, December 1964 (1964-12-01), pages 830 - 831, XP002031703 *

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE1012157A3 (fr) * 1997-03-19 2000-06-06 Hitachi Ltd Compresseur centrifuge a deux etages.
US6196809B1 (en) 1997-03-19 2001-03-06 Hitachi, Ltd. Two-stage centrifugal compressor
EP0896158A2 (fr) * 1997-08-05 1999-02-10 Corac Group plc Compresseurs
EP0896158A3 (fr) * 1997-08-05 1999-12-01 Corac Group plc Compresseurs
US6296441B1 (en) 1997-08-05 2001-10-02 Corac Group Plc Compressors
DE19917958B4 (de) * 1999-04-21 2014-03-06 Institut für Luft- und Kältetechnik gemeinnützige Gesellschaft mbH Kühleinrichtung für Elektromotoren
EP1321680A3 (fr) * 2001-12-22 2003-12-10 Miscel Oy Turbomachine
CN105782075A (zh) * 2015-01-13 2016-07-20 Lg电子株式会社 涡轮压缩机以及制冷机

Also Published As

Publication number Publication date
EP0883749B1 (fr) 2001-12-05
DE69708850D1 (de) 2002-01-17
EP0883749A1 (fr) 1998-12-16
AU1609197A (en) 1997-08-22
DE69708850T2 (de) 2002-07-18
GB9602126D0 (en) 1996-04-03
ATE210246T1 (de) 2001-12-15

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