US20100014990A1 - Compressor Unit - Google Patents

Compressor Unit Download PDF

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Publication number
US20100014990A1
US20100014990A1 US12/225,519 US22551907A US2010014990A1 US 20100014990 A1 US20100014990 A1 US 20100014990A1 US 22551907 A US22551907 A US 22551907A US 2010014990 A1 US2010014990 A1 US 2010014990A1
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US
United States
Prior art keywords
cooling
medium
stator
compressor unit
pressure
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
US12/225,519
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English (en)
Inventor
Theo Nijhuis
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.)
Siemens AG
Original Assignee
Siemens AG
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 Siemens AG filed Critical Siemens AG
Assigned to SIEMENS AKTIENGESELLSCHAFT reassignment SIEMENS AKTIENGESELLSCHAFT ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: NIJHUIS, THEO
Publication of US20100014990A1 publication Critical patent/US20100014990A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage pumps
    • F04D17/122—Multi-stage pumps the individual rotor discs being, one for each stage, on a common shaft and axially spaced, e.g. conventional centrifugal multi- stage compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • 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
    • 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
    • F04D25/0686—Units comprising pumps and their driving means the pump being electrically driven specially adapted for submerged use
    • 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
    • F04D29/5806—Cooling the drive system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
    • F04D29/584—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps cooling or heating the machine
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C37/00—Cooling of bearings
    • F16C37/005—Cooling of bearings of magnetic bearings
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K9/00—Arrangements for cooling or ventilating
    • H02K9/19—Arrangements for cooling or ventilating for machines with closed casing and closed-circuit cooling using a liquid cooling medium, e.g. oil
    • H02K9/197—Arrangements for cooling or ventilating for machines with closed casing and closed-circuit cooling using a liquid cooling medium, e.g. oil in which the rotor or stator space is fluid-tight, e.g. to provide for different cooling media for rotor and stator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/058—Bearings magnetic; electromagnetic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/44—Centrifugal pumps
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means
    • F16C32/0406—Magnetic bearings
    • F16C32/044—Active magnetic bearings
    • F16C32/0474—Active magnetic bearings for rotary movement
    • F16C32/0489—Active magnetic bearings for rotary movement with active support of five degrees of freedom, e.g. two radial magnetic bearings combined with an axial bearing

Definitions

  • the invention relates to a compressor unit for compression of a pumping medium, in particular for underwater operation, comprising a compressor and an electric motor which comprises a stator and a rotor.
  • a compressor unit of the abovementioned type is already known from international patent application WO 02/099286 A1.
  • the compressor unit described there provides, for cooling purposes, that a portion is tapped off from the pumping medium, generally natural gas, in the area of an overflow from the radial stages of the compressor and is used to pass around the components to be cooled, in such a way that the heat losses, which are in the order of magnitude of 100-200 kW, are dissipated with the cold medium to be pumped.
  • a compressor unit of the type mentioned initially is already known from EP 1 069 313 A2, whose electric motor has a separate cooling arrangement which is operated with nitrogen as a cooling medium, which is pumped in a gaseous form in the circuit by means of an additionally driven apparatus.
  • a fluid energy machine in which a cooling medium is pumped in a forced circulation by means of a pump is already known from DE 196 23 553 A1.
  • This concept for cooling the compressor unit is particularly advantageous since the pumping medium which must be transported in any case is used to dissipate the heat losses and there is no need for any additional media exchange between the compressor unit and further components of the environment.
  • this procedure results in particular difficulties owing to the aggressive chemical characteristics of the media to be pumped. While it is sufficient for flow to be passed around the rotor for cooling, further cooling measures are necessary to dissipate the heat losses for the stator.
  • a further risk is the generally porous insulation of the stator which absorbs part of the pumping medium in the area where the pumping medium flows around it, while the pumping medium is in contact with the stator as a cooling medium, in such a way that, in the event of a sudden pressure drop, for example in the case of an interruption in operation, this leads to explosive expansion of the absorbed medium in the pores of the insulation, which is in consequence destroyed.
  • the invention is therefore based on the object of providing a cooling arrangement for the stator of an electric motor of a motor-driven compressor unit, in particular for undersea operation, which on the one hand offers excellent operational reliability and on the other hand does not require any substances to be exchanged with the environment during operation.
  • a compressor unit is proposed in order to solve this problem.
  • One major advantage of the compressor unit according to the invention is that the separate cooling of the stator can be matched precisely to its operating conditions and, in particular, it is possible to take account on the one hand of the high power losses and on the other hand of the sensitivity of this component.
  • the sensitivity of the-stator to contamination is taken into account if the cooling arrangement has a closed circuit in which a cooling medium circulates.
  • One expedient development of the invention provides for the stator to be provided with cooling channels and for the pumping medium to flow through these channels for cooling. When using the pumping medium for cooling purposes, this embodiment involves the risk that the contamination of the pumping medium during the course of operation adversely affects the flow through the channels, and may also block them.
  • the stator cooling arrangement is operationally reliable because of the separate circuit according to the invention.
  • the cooling arrangement it is worthwhile for the cooling arrangement to have a condenser which is connected to the cooled stator by means of a feed line and a return line, with the cooling arrangement being designed such that the cooling medium circulates between the condenser, the return line, the stator and the feed line.
  • the circulation can be driven particularly advantageously by means of natural convection, thus resulting in a natural circulation of the cooling medium between the abovementioned components. This makes it possible to save additional pumping precautions for the cooling medium, thus reducing the complexity of the compressor unit and in this way contributing to high availability.
  • the circulation in the cooling arrangement can also be driven by means of a pump in such a way that this always results in a forced circulation.
  • the cooling medium is particularly advantageously in such a form that a phase change of at least a part of the cooling medium takes place in the circulation in the cooling arrangement. This results in the cooling performance being particularly high.
  • the pressure of the filling of the cooling medium in the closed circuit can be set such that, in operating conditions, at least a portion of the cooling medium changes to the gas phase during the heat absorption in the stator, and this portion changes back to the liquid phase during the heat emission in the condenser.
  • Ammonia, carbon dioxide and hydrocarbons are highly suitable for use as a cooling medium.
  • the hydrocarbons may be both halogenated and non-halogenated, in which case the non-halogenated hydrocarbons are advantageous over the halogenated hydrocarbons, in the same way as ammonia and carbon dioxide, for environmental compatibility reasons.
  • separate cooling for the stator of the electric motor of the compressor unit, on the one hand, and a cooling system for the further elements of the compressor unit, on the other hand, are particularly expedient.
  • the separation of the cooling from the cooling system is appropriate for the particular requirements for the heat dissipation from the stator of a compressor unit of this generic type.
  • the cooling system which, inter alia, cools the compressor and the rotor of the motor as well particularly advantageously provides the pumping medium as the cooling medium, as a result of which the heat losses are dissipated with the pumping medium
  • the pumping medium is frequently heavily contaminated and can adversely affect the operation of sensitive components as it flows around them. It is therefore worthwhile designing the bearings of the rotor, specifically the axial bearings and the radial bearings, in an encapsulated form, such that no substances are exchanged between the environment and these components. This means that magnetic bearings must be used. This also applies to the rotor and the stator, which can be protected in a similar manner by means of encapsulation against the aggressive pumping media.
  • the pressure of the pumping medium at the inlet may vary between 40 bar and 140 bar depending on the amount and yield of the deposit, and therefore that the cooling arrangement should be designed for a differential pressure of up to 200 bar if the cooling arrangement is operated just with the same cooling medium over the entire period during which the natural gas is being pumped.
  • the cooling medium is changed as a function of the pressure of the pumping medium, for example in the sequence propane, butane, freon.
  • the change in the cooling medium can advantageously be synchronized with other maintenance tasks.
  • FIG. 1 shows a schematic illustration of a longitudinal section through a compressor unit according to the invention
  • FIG. 2 shows a schematic illustration of the motor of the compressor unit with the separate cooling arrangement, as a thermosiphon.
  • FIG. 1 shows, schematically, a section along a compressor unit 1 according to the invention which has, as major components, a motor 2 and a compressor 3 in a gas-tight housing 4 .
  • the housing 4 accommodates the motor 2 and the compressor 3 .
  • the housing 4 is provided with an inlet 6 and an outlet 7 in the area of the junction between the motor 2 and the compressor 3 , with the fluid to be compressed being sucked in through the inlet 6 by means of a suction connecting stub 8 , and with the compressed fluid flowing out through the outlet 7 .
  • the compressor unit 1 is arranged vertically during operation, with a motor rotor 15 of the motor 2 above a compressor rotor 9 of the compressor 3 being combined to form a common shaft 19 which rotates about a common vertical rotation axis 60 .
  • the motor rotor 15 is borne in a first radial bearing 21 at the upper end of the motor rotor 15 .
  • the compressor rotor 9 is borne by means of a second radial bearing 22 in the lower position.
  • An axial bearing 25 is provided at the upper end of the common shaft 19 , that is to say at the upper end of the motor rotor 15 .
  • the radial bearings and the axial bearing operate electromagnetically and are each encapsulated.
  • the radial bearings extend around the respective bearing point of the shaft 19 in the circumferential direction and in this case are circumferential through 360° and are undivided.
  • the compressor 3 is in the form of a centrifugal compressor and has three compressor stages 1 which are each connected by means of an overflow 33 .
  • the pressure differences which result across the compressor stages 11 ensure that there is a thrust on the compressor rotor 9 which is transmitted on the motor rotor 15 and is directed against the force of gravity from the entire resultant rotor comprising the compressor rotor 9 and the motor rotor 15 , thus resulting in a very high degree of thrust matching during rated operation.
  • This allows the axial bearing 25 to be designed to be comparatively smaller than if the rotation axis 60 were to be arranged horizontally.
  • the electromagnetic bearings 21 , 22 , 25 are cooled to the operating temperature by means of a cooling system 31 , with the cooling system 31 providing a tap 32 in an overflow of the compressor 3 .
  • a portion of the pumping medium which is preferably natural gas, is passed from the tap 32 by means of pipelines through a fitter 35 , and is then passed through two separate pipelines to the respective outer bearing points (first radial bearing 21 and fourth radial bearing 24 as well as the axial bearing 25 ). This cooling by means of the cold pumping medium saves additional supply lines.
  • the motor rotor 15 is surrounded by a stator 16 which has encapsulation 39 such that the aggressive pumping medium does not damage the windings of the stator 16 .
  • the encapsulation is in this case preferably designed such that it can contribute to the full operating pressure. This is also because a separate cooling arrangement 40 is provided for the stator, in which cooling arrangement 40 a dedicated cooling medium 56 circulates.
  • a pump 42 in this case ensures circulation via a heat exchanger 43 , assisting the natural circulation.
  • At least the encapsulation 39 is designed such that the section which extends between the stator 16 and the motor rotor 15 , while having a thin wall thickness, is nevertheless able to withstand the design pressure when the stator cooling arrangement 40 is completely filled by means of the cooling medium 56 . This makes it possible to avoid relatively high eddy current losses in this area, thus improving the efficiency of the overall arrangement.
  • the pressure of the filling or the cooling medium 56 in the stator cooling arrangement 40 can be matched such that the encapsulation is always operated in the design range of the pressure difference.
  • the cooling medium 56 can be correspondingly changed during maintenance tasks, for example in the sequence from propane to butane to freon, in the sequence of falling pressure.
  • the compressor rotor 9 expediently has a compressor shaft 10 on which the individual compressor stages 11 are mounted. This can preferably be done by means of a thermal shrink fit. An interlock, for example by means of polygons, is likewise possible. Another embodiment provides for different compressor stages 11 to be welded to one another, thus resulting in an integral compressor rotor 9 .
  • FIG. 2 shows the motor rotor 15 , the stator 16 and the cooling arrangement 40 .
  • the cooling arrangement 40 has a cooling circuit 50 which extends through cooling channels 51 , collecting areas 52 arranged on both sides of the cooling channels 51 , into lines which connect these collecting areas, specifically a feed line 53 and a return line 54 , as well as a condenser 55 arranged between the feed line 53 and the return line 54 .
  • the cooling medium 56 for example a hydrocarbon, starts to flow in cooling channels 51 of the stator 16 , flows through the feed line 53 into the condenser 55 where the cooling medium 56 is condensed, and then flows as a liquid through the return line 54 into a collecting area 52 which is located at the return end of the cooling channels 51 .
  • the circuit is closed and the pressure and the amount with which it is filled are chosen such that a phase change takes place between the feed and return.
  • the temperature difference between the feed and the return is preferably 10 K.
  • the condenser is located geodetically at the highest point (height difference ⁇ H), thus allowing a natural circulation.
  • a pump 42 can be arranged in the return to assist this.
  • the stator is encapsulated, and cooling by means of the pumping medium 80 which flows around the rotor 15 takes place in a gap between the rotor 15 and the stator 16 .

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Power Engineering (AREA)
  • Motor Or Generator Cooling System (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Compressor (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
US12/225,519 2006-03-24 2007-02-19 Compressor Unit Abandoned US20100014990A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP06006066.2 2006-03-24
EP06006066 2006-03-24
PCT/EP2007/051539 WO2007110281A1 (de) 2006-03-24 2007-02-19 Verdichtereinheit

Publications (1)

Publication Number Publication Date
US20100014990A1 true US20100014990A1 (en) 2010-01-21

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ID=38032746

Family Applications (1)

Application Number Title Priority Date Filing Date
US12/225,519 Abandoned US20100014990A1 (en) 2006-03-24 2007-02-19 Compressor Unit

Country Status (11)

Country Link
US (1) US20100014990A1 (de)
EP (1) EP1999375B1 (de)
JP (1) JP2009530537A (de)
CN (1) CN101410624B (de)
AT (1) ATE506542T1 (de)
BR (1) BRPI0709131A2 (de)
DE (1) DE502007006992D1 (de)
ES (1) ES2364588T3 (de)
NO (1) NO20084448L (de)
RU (1) RU2410572C2 (de)
WO (1) WO2007110281A1 (de)

Cited By (9)

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Publication number Priority date Publication date Assignee Title
US20120107143A1 (en) * 2010-10-27 2012-05-03 Dresser-Rand Company Method and system for cooling a motor-compressor with a closed-loop cooling circuit
US20130136629A1 (en) * 2011-06-01 2013-05-30 Dresser-Rand Company Subsea motor-compressor cooling system
US20130302184A1 (en) * 2011-05-31 2013-11-14 Carrier Corporation Compressor Windage Mitigation
US20170298755A1 (en) * 2015-02-23 2017-10-19 Mitsubishi Heavy Industries, Ltd. Compressor system
WO2018024699A1 (de) * 2016-08-04 2018-02-08 Siemens Aktiengesellschaft Elektrische maschine mit effizienterer kühlung
US20180038389A1 (en) * 2015-03-20 2018-02-08 Mitsubishi Heavy Industries, Ltd. Compressor system, and attachment structure for centrifugal separator
WO2018043797A1 (ko) * 2016-08-30 2018-03-08 엘지전자 주식회사 압축기 및 그것을 포함하는 칠러 시스템
US10711799B2 (en) 2012-05-09 2020-07-14 Nuovo Pignone Srl Pressure equalizer
EP3121449B1 (de) * 2015-07-22 2022-10-05 Thermodyn Unterwasserradialverdichter mit horizontaler welle und mit lediglich einem axialschublager

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ES2392189T3 (es) 2007-11-30 2012-12-05 Siemens Aktiengesellschaft Procedimiento para el funcionamiento de un dispositivo compresor y dispositivo compresor correspondiente
EP2103810A1 (de) * 2008-03-19 2009-09-23 Siemens Aktiengesellschaft Kompressoreinheit
EP2113671A1 (de) 2008-04-28 2009-11-04 Siemens Aktiengesellschaft Anordnung mit einem elektrischen Motor und einer Pumpe
DE102009021098A1 (de) * 2009-05-13 2010-11-18 Siemens Aktiengesellschaft Elektrisches Antriebssystem
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DE102009054773A1 (de) * 2009-12-16 2011-06-22 Piller Industrieventilatoren GmbH, 37186 Turboverdichter und Verdichteranlage umfassend einen derartigen Turboverdichter
IT1396885B1 (it) * 2009-12-17 2012-12-20 Nuovo Pignone Spa Cuscinetto a gas intermedio
DE102010039732A1 (de) 2010-08-25 2012-03-01 Siemens Aktiengesellschaft Fluidenergiemaschine
DE102012207019B4 (de) * 2012-04-27 2015-12-24 Siemens Aktiengesellschaft Strömungsmaschine sowie Verfahren zur Kühlen einer solchen
GB2513664B (en) * 2013-05-03 2016-01-06 Dyson Technology Ltd Compressor
BR112016009943B1 (pt) 2014-02-19 2022-08-02 Sulzer Management Ag Máquina rotativa, uso da máquina rotativa e processo para a troca de calor em uma máquina rotativa
WO2016136043A1 (ja) * 2015-02-23 2016-09-01 三菱重工業株式会社 圧縮機システム
CN105207414A (zh) * 2015-09-28 2015-12-30 无锡市南方防爆电机有限公司 一种降温式防爆电机
CN105351221B (zh) * 2015-12-15 2018-06-05 中国科学院合肥物质科学研究院 一种耐高温高压无泄漏离心式压缩机
CN108054874B (zh) * 2017-12-14 2019-10-22 胡美玉 一种封闭式氨制冷压缩机用耐氨电机
KR102052707B1 (ko) * 2018-05-15 2019-12-05 엘지전자 주식회사 냉각유로를 구비하는 터보 압축기
DE112019002451T5 (de) 2018-05-15 2021-03-04 Lg Electronics Inc. Turboverdichter
CN111946600A (zh) * 2020-08-04 2020-11-17 蚌埠艾普压缩机制造有限公司 一种氢气压缩机水腔降温方法

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Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9200643B2 (en) * 2010-10-27 2015-12-01 Dresser-Rand Company Method and system for cooling a motor-compressor with a closed-loop cooling circuit
US20120107143A1 (en) * 2010-10-27 2012-05-03 Dresser-Rand Company Method and system for cooling a motor-compressor with a closed-loop cooling circuit
US10612551B2 (en) * 2011-05-31 2020-04-07 Carrier Corporation Compressor motor windage loss mitigation
US20130302184A1 (en) * 2011-05-31 2013-11-14 Carrier Corporation Compressor Windage Mitigation
CN103562553A (zh) * 2011-05-31 2014-02-05 开利公司 压缩机风阻减轻
US20130136629A1 (en) * 2011-06-01 2013-05-30 Dresser-Rand Company Subsea motor-compressor cooling system
US9206819B2 (en) * 2011-06-01 2015-12-08 Dresser-Rand Company Subsea motor-compressor cooling system
US10711799B2 (en) 2012-05-09 2020-07-14 Nuovo Pignone Srl Pressure equalizer
US20170298755A1 (en) * 2015-02-23 2017-10-19 Mitsubishi Heavy Industries, Ltd. Compressor system
US20180038389A1 (en) * 2015-03-20 2018-02-08 Mitsubishi Heavy Industries, Ltd. Compressor system, and attachment structure for centrifugal separator
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CN101410624A (zh) 2009-04-15
EP1999375A1 (de) 2008-12-10
BRPI0709131A2 (pt) 2011-06-28
NO20084448L (no) 2008-12-17
WO2007110281A1 (de) 2007-10-04
JP2009530537A (ja) 2009-08-27
CN101410624B (zh) 2011-03-02
EP1999375B1 (de) 2011-04-20
ES2364588T3 (es) 2011-09-07
RU2008142102A (ru) 2010-04-27
DE502007006992D1 (de) 2011-06-01
RU2410572C2 (ru) 2011-01-27
ATE506542T1 (de) 2011-05-15

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