US20040146414A1 - Screw compressor with switched reluctance motor - Google Patents

Screw compressor with switched reluctance motor Download PDF

Info

Publication number
US20040146414A1
US20040146414A1 US10/480,157 US48015703A US2004146414A1 US 20040146414 A1 US20040146414 A1 US 20040146414A1 US 48015703 A US48015703 A US 48015703A US 2004146414 A1 US2004146414 A1 US 2004146414A1
Authority
US
United States
Prior art keywords
rotor
motor
screw
compressor
screw 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.)
Abandoned
Application number
US10/480,157
Other languages
English (en)
Inventor
Philip Nichol
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.)
Compair UK Ltd
Original Assignee
Individual
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 Individual filed Critical Individual
Assigned to COMPAIR UK LIMITED reassignment COMPAIR UK LIMITED ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: NICHOL, PHILIP
Publication of US20040146414A1 publication Critical patent/US20040146414A1/en
Abandoned legal-status Critical Current

Links

Images

Classifications

    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/08—Structural association with bearings
    • H02K7/09—Structural association with bearings with magnetic bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/102—Adjustment of the interstices between moving and fixed parts of the machine by means other than fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/0085—Prime movers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/51—Bearings for cantilever assemblies
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/08—Structural association with bearings
    • H02K7/085—Structural association with bearings radially supporting the rotary shaft at only one end of the rotor
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/14—Structural association with mechanical loads, e.g. with hand-held machine tools or fans

Definitions

  • the invention relates to improvements in compressors and in particular to arrangements for driving screw compressors by switched reluctance drive motors.
  • Screw compressors are used in a variety of different applications for delivering compressed air, or other gasses, at a required pressure and volume.
  • the speed at which the one or more stages of the compressor is driven is determined by the delivery requirements.
  • Induction motors are currently used to drive the majority of industrial screw compressors.
  • the design of such motors has a major effect on its behaviour and performance and seldom has it been possible to match the compressor speed with the speeds available from standard induction motors.
  • a belt drive system or gearbox is used. Then, by changing the drive ratio, a number of discrete outputs may be obtained for running a compressor at different speeds.
  • inverter drives with induction motors have meant that standard motors may be run at infinitely variable speeds within the capabilities of the motors. Due to the use of induction motors this still means that there is an upper limit on the speed determined by the design of the motor. For example two pole motors run normally at around 3600 rpm on a 60 Hz supply with the use of an inverter they may be run to perhaps 4500 rpm, depending on the motor design. In small screw compressors speeds in excess of this are commonly required.
  • the induction motor is a self-contained unit coupled to the compressor through a flexible coupling.
  • induction motors are air-cooled which, when used with a rotary compressor, gives rise to fan losses and can lead to possible damage to the motor-due to air borne contaminants.
  • the noise generated by the fan is a significant contributor to the noise of the motor especially at high speeds.
  • EP-A-1041289 recognises the need to dispense with a gear assembly in a compressor assembly and to provide a direct link between the compressor and motor. It therefore describes a rotary compressor driven by a switched reluctance motor, wherein the impeller of the compressor is mounted on a drive shaft assembly, on which the rotor of the switched reluctance motor is also mounted.
  • EP-A-1041289 is specifically directed towards a two stage centrifugal or axial flow compressor as opposed to a screw compressor. Centrifugal compressors operate in a very different speed range to screw compressors, generally in excess of 50,000 rpm, whereas most screw compressors operate at below 25,000 rpm.
  • the invention therefore provides a screw compressor assembly for providing compressed gas comprising a screw compressor having a casing and at least one pair of intermeshing helically formed screw rotors each of which is mounted on a rotor shaft rotatably mounted within the casing by means of bearings, said assembly further comprising a switched reluctance motor comprising a stator attached to the casing and a rotor mounted on one of the rotor shafts such that one of the screw rotors is driven directly by the motor, wherein the motor rotor is displaced relative to the stator by a predetermined axial distance such that a resultant magnetic force is provided in an axial direction.
  • the design of the motor can be matched to the characteristics of the screw compressor in terms of torque and speed.
  • the switched reluctance motor may also be designed to run at almost any speed and its speed is infinitely variable within its designed speed range.
  • An additional benefit is that the axial magnetic forces available from the rotor of the motor are used to affect the axial bearing loads in the compressor.
  • the cooling liquid for the compressor may be circulated around the stator of the motor to provide cooling for the motor. This has the benefit over an air-cooled motor of being able to seal the motor thus reducing noise (especially important in high-speed drives) and improving reliability.
  • FIG. 1 is a cross-sectional front elevation of a section of a rotary screw compressor according to the invention showing the mounting of the switched reluctance drive motor with the motor rotor displaced away from the compressor;
  • FIG. 2 is a schematic of the screw compressor of the present invention.
  • FIG. 3 is similar to FIG. 1, but shows the motor rotor displaced in the opposite direction.
  • FIGS. 1 and 2 The embodiment of the invention illustrated in FIGS. 1 and 2 is a single stage liquid-injected screw compressor assembly, although most of the features may be applied to an oil-free screw compressor or other types of single or multi-stage screw compressor.
  • FIG. 1 shows a section of a single stage liquid-injected screw compressor ( 10 ) consisting of a pair of contra-rotating, helically cut fluted rotors ( 11 , 12 ) mounted respectively on rotor shafts ( 13 , 14 ) which are supported at each end in rolling bearings ( 15 ) in a rigid compressor casing ( 16 ).
  • One of the rotor shafts ( 13 ), on which a “driven” rotor ( 11 ) is mounted is extended with respect to the other rotor shaft ( 14 ).
  • the drive motor ( 17 ) used to drive the compressor ( 10 ) is a switched reluctance motor.
  • Switched reluctance motors suitable for use in the present invention are already known in the art, such as described in EP-A-0702448.
  • both the stator ( 18 ) and the rotor ( 19 ) have projecting poles.
  • the rotor ( 19 ) has no permanent magnets or windings.
  • the rotor ( 19 ) of the switched reluctance motor ( 17 ) is attached to the extended rotor shaft ( 13 ) using a locking system, such as a taper or a parallel shaft with a key, to ensure concentricity and transmission of torque.
  • the rotor ( 19 ) has no bearings and is overhung and therefore entirely supported by the compressor bearings ( 15 ).
  • the stator ( 18 ) is attached to the compressor casing ( 16 ) so that it is concentric to the motor rotor ( 19 ).
  • a magnetic field is generated in the motor stator ( 18 ) which causes the motor rotor ( 19 ) to turn which rotates the driven compressor rotor ( 11 ).
  • the motor ( 17 ) is connected to a power converter ( 20 ), in which a three phase electrical supply is rectified to produce dc voltage, which is then switched to the stator windings in a controlled manner to generate the necessary torque to produce the required rotational speed.
  • the speed may be set to a fixed value manually or varied to maintain a specific value, calculated by a controller ( 30 ) to maintain a parameter such as compressor pressure within certain pre-set limits.
  • the rotation of the driven compressor rotor ( 11 ) transfers drive to the second rotor ( 12 ). This action induces air into the compressor ( 10 ) through a filter ( 32 ) via an inlet port at an inlet end of the compressor ( 10 ). As the rotors ( 11 , 12 ) continue to rotate the reduction in the volume between them and the casing ( 16 ) causes the trapped volume of air to be compressed.
  • the compressor ( 10 ) is preferably driven at a speed lying in the range of 500 to 25,000 rpm and more preferably in the range of 1000 to 10,000 rpm. The compressed air is expelled via a delivery port at the delivery end of the compressor ( 10 ).
  • liquid is injected into the compressor ( 10 ) during compression to cool, seal and lubricate the compressor ( 10 ).
  • the compressed air/liquid mixture is passed to a separator vessel ( 21 ) where the liquid is separated and the air leaves the compressor ( 10 ) at a compressor outlet ( 22 ) usually through a non-return valve ( 23 ) and aftercooler ( 24 ).
  • a small amount of liquid which has coalesced in the separator ( 21 ) is returned to the compressor ( 10 ) via a scavenge line ( 33 ) and strainer ( 34 ).
  • the rest of the coolant liquid is passed, due to differential pressure in the system, from the separator vessel ( 21 ) through a radiator ( 25 ) and is then used to cool the stator ( 18 ) of the motor by passing through a cooling jacket ( 26 ), which is in close proximity to the stator windings. From the motor cooling jacket ( 26 ) the coolant is passed through a filter ( 27 ) and then back to the compressor ( 10 ) where the coolant is injected into the compressed air and is used to lubricate the compressor bearings ( 15 ).
  • the motor air over or through the motor windings.
  • pressure is sensed at the compressor delivery point by a pressure transmitter ( 31 ). This signal is passed to the controller ( 30 ) which in turn operates the power converter ( 20 ) to increase or reduce the speed of the motor until the desired pressure is reached.
  • the bearings ( 15 ) that support the rotors ( 11 , 12 ) are designed to absorb radial and axial loads.
  • the radial and axial loads are produced from a number of sources including gas loads, drive force resultants and the weight of the rotating parts.
  • the dominant load is often an axial force on the rotors ( 11 , 12 ) acting from the delivery end towards the inlet end of the rotors ( 11 , 12 ).
  • the load on the axial load-carrying bearings ( 15 ) has been off-set by a number of means such as using the axial component of the thrust of a helical drive gear or by using a balance piston arrangement fed by either pressurised air or lubricant.
  • the axial loads are offset by arranging the position of the motor rotor ( 19 ) within the stator ( 18 ) so that there is a resultant magnetic force acting in the desired direction. This force can be generated where the motor rotor ( 19 ) is designed to run offset from the centre of the magnetic field generator in the stator windings.
  • This force can be produced to act in either direction depending on the axial position of the rotor ( 19 ) relative to the stator ( 18 ). In the preferred embodiment of the invention this force acts towards the delivery end of the driven rotor ( 11 ) to relieve the effects of the axial gas thrust on the delivery end axially loaded bearing of the driven rotor ( 11 ).
  • the gas loads caused by compression will act towards the compressor inlet end, that is towards the motor ( 17 ) and the axial loads generated by the flux in the motor ( 17 ) will be opposite, that is towards the compressor rotors ( 11 , 12 ).
  • the axial forces generated in the motor ( 17 ) increase as the applied torque increases.
  • the axial loads on the bearings ( 15 ) will increase with increasing pressure and speed which corresponds with torque.
  • the load on the compressor axial bearings ( 15 ) caused by the gas loads and drive load components will be offset by the opposite acting magnetic loads from the motor rotor ( 19 ).
  • An enhancement of this embodiment of the invention is where the axial forces on the motor rotor ( 19 ), which are known in the art to be cyclic, are produced so as to be in phase with the cyclic axial loads from the compressor rotors ( 11 , 12 ).
  • the maximum axial load is known to take place at the point before the trapped volume of gas is released into the delivery port. The number of times this takes place in a revolution is dependent on the number of lobes on the male rotor, i.e. for a four-lobed male rotor there will be four peaks per revolution.
  • the axial force exerted by the stator ( 18 ) flux on the motor rotor ( 19 ) can also be used to increase the load on the axial bearings ( 15 ) in the compressor ( 10 ) on start-up to ensure that the rotor ( 19 ) does not contact the end face of the compressor casing bore. This is shown in FIG. 3.
  • the weight of the rotor ( 11 ) can tend to allow it to drop when stationary due to the slope of the bearing race. This can then allow the end of the rotor ( 11 ) to contact the casing. Under conditions of marginal lubrication this can result in the rotor ( 11 ) contacting the casing and causing wear during starting.
  • the motor rotor ( 19 ) is designed to be offset in the stator ( 18 ) by an amount corresponding to the movement of the rotor in the bearing (typically ⁇ 0.2 mm).
  • the flux in the winding draws the motor rotor ( 19 ) with the compressor rotor ( 11 ) attached towards the inlet end of the compressor ( 10 ) thus moving the compressor rotor ( 11 ) away from the delivery end face of the casing bore.
  • the motor rotor ( 19 ) returns to its neutral axial position the axial forces diminishes and the compressor ( 10 ) runs normally.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Power Engineering (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
US10/480,157 2001-06-11 2002-06-10 Screw compressor with switched reluctance motor Abandoned US20040146414A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
GB0114149.8 2001-06-11
GB0114149A GB2376505B (en) 2001-06-11 2001-06-11 Improvements in screw compressors
PCT/GB2002/002641 WO2002101244A1 (en) 2001-06-11 2002-06-10 Screw compressor with switched reluctance motor

Publications (1)

Publication Number Publication Date
US20040146414A1 true US20040146414A1 (en) 2004-07-29

Family

ID=9916311

Family Applications (1)

Application Number Title Priority Date Filing Date
US10/480,157 Abandoned US20040146414A1 (en) 2001-06-11 2002-06-10 Screw compressor with switched reluctance motor

Country Status (8)

Country Link
US (1) US20040146414A1 (de)
EP (1) EP1395756B1 (de)
AT (1) ATE309467T1 (de)
AU (1) AU2002345155B2 (de)
DE (1) DE60207246T2 (de)
ES (1) ES2252475T3 (de)
GB (1) GB2376505B (de)
WO (1) WO2002101244A1 (de)

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20070207045A1 (en) * 2003-10-17 2007-09-06 Mats Sundstrom Compressor
US20070241627A1 (en) * 2006-04-12 2007-10-18 Sullair Corporation Lubricant cooled integrated motor/compressor design
US20080181798A1 (en) * 2007-01-29 2008-07-31 Victory Rig Equipment Corporation Fluid pump drive
US20090010774A1 (en) * 2007-07-02 2009-01-08 Fish Robert D Air Compressor and Reservoir For Topping Off Low Pressure Tires
CN102748285A (zh) * 2012-04-11 2012-10-24 无锡市制冷设备厂有限责任公司 一种螺杆压缩机
US20130115042A1 (en) * 2009-12-22 2013-05-09 Gabriele Mariotti Dynamic thrust balancing for centrifugal compressors
JP2013150399A (ja) * 2012-01-17 2013-08-01 Asmo Co Ltd 電動ポンプ
US20140271280A1 (en) * 2013-03-15 2014-09-18 Merkle-Korff Industries, Inc. Pump motor
US20150030491A1 (en) * 2012-02-28 2015-01-29 Atlas Copco Airpower, Naamloze Vennootschap Compressor device as well as the use of such a compressor device
CN104343663A (zh) * 2013-07-23 2015-02-11 复盛股份有限公司 空气压缩系统及其冷却结构
CN104929936A (zh) * 2015-06-24 2015-09-23 煤科集团沈阳研究院有限公司 一种矿用封闭式螺杆制冷压缩机
US20150300355A1 (en) * 2012-10-29 2015-10-22 Pierburg Pump Technology Gmbh Automotive electric liquid pump
US9732747B2 (en) 2013-07-17 2017-08-15 Fusheng Industrial Co., Ltd. Air compression system and cooling structure thereof
US10197058B2 (en) 2012-02-28 2019-02-05 Atlas Copco Airpower, Naamloze Vennootschap Screw compressor
US10941770B2 (en) 2010-07-20 2021-03-09 Trane International Inc. Variable capacity screw compressor and method
US10947976B2 (en) * 2015-12-17 2021-03-16 Kobe Steel, Ltd. Screw compressor
US11015602B2 (en) 2012-02-28 2021-05-25 Atlas Copco Airpower, Naamloze Vennootschap Screw compressor
CN113027758A (zh) * 2021-02-26 2021-06-25 珠海格力电器股份有限公司 压缩机及空调
US20220243959A1 (en) * 2021-02-01 2022-08-04 Reed Harmon Carpenter Chiller system with direct-drive switched reluctance motor
US20250122877A1 (en) * 2021-08-12 2025-04-17 Atlas Copco Airpower, Naamloze Vennootschap Compressor assembly comprising a motor driving one or more compressor rotors and method for fabricating a housing part of such a compressor assembly

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2370320A (en) * 2000-12-21 2002-06-26 Ingersoll Rand Europ Sales Ltd Compressor and driving motor assembly
US7202626B2 (en) 2005-05-06 2007-04-10 York International Corporation Variable speed drive for a chiller system with a switched reluctance motor
US7439702B2 (en) 2005-11-15 2008-10-21 York International Corporation Application of a switched reluctance motion control system in a chiller system
US7559298B2 (en) 2006-04-18 2009-07-14 Cleeves Engines Inc. Internal combustion engine
JP5410369B2 (ja) * 2010-05-31 2014-02-05 株式会社神戸製鋼所 スクリュ圧縮機
BE1019398A3 (nl) * 2010-07-02 2012-06-05 Atlas Copco Airpower Nv Compressorelement van een schroefcompressor.
DE102011054607A1 (de) * 2010-10-27 2012-06-21 Gebr. Becker Gmbh Vakuumpumpe
AT511480B1 (de) * 2011-05-31 2014-02-15 Johannes Kepler Uni Linz Elektrische maschine mit einem magnetisch gelagerten reluktanzläufer
JP2017158333A (ja) * 2016-03-02 2017-09-07 株式会社神戸製鋼所 電動機
BE1024712B1 (nl) * 2016-11-03 2018-06-07 Atlas Copco Airpower Nv Aandrijving voor een compressorelement en watergeïnjecteerde compressorinrichting daarmee uitgerust
CN106703894A (zh) * 2016-12-30 2017-05-24 山西易通环能科技集团有限公司 一种用于低温发电的半封闭螺杆动力机
CN111963427B (zh) 2019-05-20 2022-06-14 复盛实业(上海)有限公司 螺旋式压缩机

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3432089A (en) * 1965-10-12 1969-03-11 Svenska Rotor Maskiner Ab Screw rotor machine for an elastic working medium
US4746277A (en) * 1986-01-31 1988-05-24 Stal Refrigeration Ab Rotary compressor with pressure pulse suppression
US5222874A (en) * 1991-01-09 1993-06-29 Sullair Corporation Lubricant cooled electric drive motor for a compressor
US5246349A (en) * 1991-03-18 1993-09-21 Sullair Corporation Variable reluctance electric motor driven vacuum pump
US5314312A (en) * 1992-01-31 1994-05-24 Matsushita Electric Industrial Co., Ltd. Fluid-rotating apparatus
US5599176A (en) * 1994-02-05 1997-02-04 Man Gutehoffnungshutte Aktiengesellschaft Threaded-rotor compressor
US6093007A (en) * 1995-10-30 2000-07-25 Shaw; David N. Multi-rotor helical-screw compressor with thrust balance device
US6287088B1 (en) * 1998-09-17 2001-09-11 Hitachi, Ltd. Oil free screw compressor
US6328540B1 (en) * 1999-06-09 2001-12-11 Sterling Fluid Systems (Germany) Gmbh Rotary piston compressor with an axial direction of delivery
US6371739B1 (en) * 1999-01-22 2002-04-16 Matsushita Electric Industrial Co., Ltd. Method and apparatus for applying pre-load to the bearing structure of a drive shaft that is directly driven by an electric motor
US6506031B2 (en) * 2001-04-04 2003-01-14 Carrier Corporation Screw compressor with axial thrust balancing and motor cooling device

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH664604A5 (fr) * 1985-11-25 1988-03-15 Cerac Inst Sa Machine rotative.
DE4111466A1 (de) * 1991-04-09 1992-10-15 Speck Pumpenfabrik Walter Spec Kreiselpumpe mit spaltrohrmotor
GB9418710D0 (en) 1994-09-16 1994-11-02 Switched Reluctance Drives Ltd Stator for electric machine and lamination thereof
US6015272A (en) * 1996-06-26 2000-01-18 University Of Pittsburgh Magnetically suspended miniature fluid pump and method of designing the same
US6193473B1 (en) 1999-03-31 2001-02-27 Cooper Turbocompressor, Inc. Direct drive compressor assembly with switched reluctance motor drive
JP2001050161A (ja) * 1999-08-05 2001-02-23 Ebara Corp 気体移送機
JP2001207984A (ja) * 1999-11-17 2001-08-03 Teijin Seiki Co Ltd 真空排気装置
DE10042545A1 (de) * 2000-08-30 2002-03-14 Rafael Weisz Integrierter Motor-Kompressor (integrierte Motor-Pumpe)

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3432089A (en) * 1965-10-12 1969-03-11 Svenska Rotor Maskiner Ab Screw rotor machine for an elastic working medium
US4746277A (en) * 1986-01-31 1988-05-24 Stal Refrigeration Ab Rotary compressor with pressure pulse suppression
US5222874A (en) * 1991-01-09 1993-06-29 Sullair Corporation Lubricant cooled electric drive motor for a compressor
US5246349A (en) * 1991-03-18 1993-09-21 Sullair Corporation Variable reluctance electric motor driven vacuum pump
US5314312A (en) * 1992-01-31 1994-05-24 Matsushita Electric Industrial Co., Ltd. Fluid-rotating apparatus
US5599176A (en) * 1994-02-05 1997-02-04 Man Gutehoffnungshutte Aktiengesellschaft Threaded-rotor compressor
US6093007A (en) * 1995-10-30 2000-07-25 Shaw; David N. Multi-rotor helical-screw compressor with thrust balance device
US6287088B1 (en) * 1998-09-17 2001-09-11 Hitachi, Ltd. Oil free screw compressor
US6371739B1 (en) * 1999-01-22 2002-04-16 Matsushita Electric Industrial Co., Ltd. Method and apparatus for applying pre-load to the bearing structure of a drive shaft that is directly driven by an electric motor
US6328540B1 (en) * 1999-06-09 2001-12-11 Sterling Fluid Systems (Germany) Gmbh Rotary piston compressor with an axial direction of delivery
US6506031B2 (en) * 2001-04-04 2003-01-14 Carrier Corporation Screw compressor with axial thrust balancing and motor cooling device

Cited By (29)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20070207045A1 (en) * 2003-10-17 2007-09-06 Mats Sundstrom Compressor
US20070241627A1 (en) * 2006-04-12 2007-10-18 Sullair Corporation Lubricant cooled integrated motor/compressor design
US20080181798A1 (en) * 2007-01-29 2008-07-31 Victory Rig Equipment Corporation Fluid pump drive
US20170190322A1 (en) * 2007-07-02 2017-07-06 Robert D. Fish Air compressor and reservioir for topping off low pressure tires
US20090010774A1 (en) * 2007-07-02 2009-01-08 Fish Robert D Air Compressor and Reservoir For Topping Off Low Pressure Tires
US20130115042A1 (en) * 2009-12-22 2013-05-09 Gabriele Mariotti Dynamic thrust balancing for centrifugal compressors
US11933301B2 (en) 2010-07-20 2024-03-19 Trane International Inc. Variable capacity screw compressor and method
US11486396B2 (en) 2010-07-20 2022-11-01 Trane International Inc. Variable capacity screw compressor and method
US11022117B2 (en) 2010-07-20 2021-06-01 Trane International Inc. Variable capacity screw compressor and method
US10941770B2 (en) 2010-07-20 2021-03-09 Trane International Inc. Variable capacity screw compressor and method
JP2013150399A (ja) * 2012-01-17 2013-08-01 Asmo Co Ltd 電動ポンプ
US10151313B2 (en) * 2012-02-28 2018-12-11 Atlas Copco Airpower, Naamloze Vennootschap Compressor device as well as the use of such a compressor device
US11015602B2 (en) 2012-02-28 2021-05-25 Atlas Copco Airpower, Naamloze Vennootschap Screw compressor
US20150030491A1 (en) * 2012-02-28 2015-01-29 Atlas Copco Airpower, Naamloze Vennootschap Compressor device as well as the use of such a compressor device
US10480511B2 (en) 2012-02-28 2019-11-19 Atlas Copco Airpower, Naamloze Vennootschap Screw compressor
US10197058B2 (en) 2012-02-28 2019-02-05 Atlas Copco Airpower, Naamloze Vennootschap Screw compressor
CN102748285A (zh) * 2012-04-11 2012-10-24 无锡市制冷设备厂有限责任公司 一种螺杆压缩机
US10590935B2 (en) * 2012-10-29 2020-03-17 Pierburg Pump Technology Gmbh Automotive electric liquid pump
US20150300355A1 (en) * 2012-10-29 2015-10-22 Pierburg Pump Technology Gmbh Automotive electric liquid pump
US20140271280A1 (en) * 2013-03-15 2014-09-18 Merkle-Korff Industries, Inc. Pump motor
US9732747B2 (en) 2013-07-17 2017-08-15 Fusheng Industrial Co., Ltd. Air compression system and cooling structure thereof
CN104343663A (zh) * 2013-07-23 2015-02-11 复盛股份有限公司 空气压缩系统及其冷却结构
CN104929936A (zh) * 2015-06-24 2015-09-23 煤科集团沈阳研究院有限公司 一种矿用封闭式螺杆制冷压缩机
US10947976B2 (en) * 2015-12-17 2021-03-16 Kobe Steel, Ltd. Screw compressor
US11781787B2 (en) * 2021-02-01 2023-10-10 Reed Harmon Carpenter Chiller system with direct-drive switched reluctance motor
US20220243959A1 (en) * 2021-02-01 2022-08-04 Reed Harmon Carpenter Chiller system with direct-drive switched reluctance motor
CN113027758A (zh) * 2021-02-26 2021-06-25 珠海格力电器股份有限公司 压缩机及空调
US20250122877A1 (en) * 2021-08-12 2025-04-17 Atlas Copco Airpower, Naamloze Vennootschap Compressor assembly comprising a motor driving one or more compressor rotors and method for fabricating a housing part of such a compressor assembly
US12590586B2 (en) * 2021-08-12 2026-03-31 Atlas Copco Airpower, Naamloze Vennootschap Compressor assembly comprising a motor driving one or more compressor rotors and method for fabricating a housing part of such a compressor assembly

Also Published As

Publication number Publication date
AU2002345155B2 (en) 2007-02-08
EP1395756A1 (de) 2004-03-10
ES2252475T3 (es) 2006-05-16
DE60207246T2 (de) 2006-08-03
WO2002101244A1 (en) 2002-12-19
DE60207246D1 (de) 2005-12-15
GB0114149D0 (en) 2001-08-01
GB2376505A (en) 2002-12-18
GB2376505B (en) 2003-12-17
EP1395756B1 (de) 2005-11-09
ATE309467T1 (de) 2005-11-15

Similar Documents

Publication Publication Date Title
EP1395756B1 (de) Schraubenverdichter mit einem motor mit geschalteter reluktanz
AU2002345155A1 (en) Screw compressor with switched reluctance motor
US6616421B2 (en) Direct drive compressor assembly
US6761542B2 (en) Multishaft electric motor and positive-displacement pump combined with such multishaft electric motor
CN100543308C (zh) 无油润滑螺旋式压缩机
US5246349A (en) Variable reluctance electric motor driven vacuum pump
EP0749533B1 (de) Verdichter
WO2002086324A3 (en) Multi-stage centrifugal compressor
KR102207772B1 (ko) 원통 대칭형 용적 기계
EP0667934B1 (de) Verdichter
US10174760B2 (en) Gear pump
US20030152468A1 (en) Vacuum pump with two co-operating rotors
JP2669676B2 (ja) トロコイド型オイルポンプ
FI103296B (fi) Menetelmä ylipaineisen kaasun tuottamiseksi
KR102036201B1 (ko) 터보 압축기
US20240360830A1 (en) Compressor assembly
Kashin et al. Advanced Axial Pumps for Oil Industry
WO2020231897A1 (en) Compressor with thrust control

Legal Events

Date Code Title Description
AS Assignment

Owner name: COMPAIR UK LIMITED, UNITED KINGDOM

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:NICHOL, PHILIP;REEL/FRAME:014985/0340

Effective date: 20031219

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION