WO2019133725A1 - Placement de palier de butée pour compresseur - Google Patents

Placement de palier de butée pour compresseur Download PDF

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Publication number
WO2019133725A1
WO2019133725A1 PCT/US2018/067710 US2018067710W WO2019133725A1 WO 2019133725 A1 WO2019133725 A1 WO 2019133725A1 US 2018067710 W US2018067710 W US 2018067710W WO 2019133725 A1 WO2019133725 A1 WO 2019133725A1
Authority
WO
WIPO (PCT)
Prior art keywords
compressor
shaft
thrust bearing
impeller
motor
Prior art date
Application number
PCT/US2018/067710
Other languages
English (en)
Inventor
Matthew Lee HEISEY
Paul William SNELL
Original Assignee
Johnson Controls Technology Company
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 Johnson Controls Technology Company filed Critical Johnson Controls Technology Company
Publication of WO2019133725A1 publication Critical patent/WO2019133725A1/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
    • 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
    • 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
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/041—Axial thrust balancing
    • F04D29/0413—Axial thrust balancing hydrostatic; hydrodynamic thrust 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
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • 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
    • F04D29/051—Axial thrust balancing
    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/06—Lubrication
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • 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
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps
    • F04D29/162—Sealings between pressure and suction sides especially adapted for elastic fluid pumps of a centrifugal flow wheel

Definitions

  • This application relates generally to vapor compression systems such as chillers, and more specifically to a compressor of a chiller.
  • Vapor compression systems utilize a working fluid, typically referred to as a refrigerant, which changes phase between vapor, liquid, and combinations thereof in response to being subjected to different temperatures and pressures associated with operation of the vapor compression system.
  • a heating, ventilation, air conditioning, and refrigeration (HVAC&R) system may include a chiller, which is a type of vapor compression system that cycles a refrigerant to remove heat from, or cool, a flow of water traversing tubes that extend through a chiller evaporator. The chilled water flow may be directed to nearby structures to absorb heat, or provide cooling, before being cycled back to the chiller evaporator to be cooled once again.
  • Chillers utilize compressors, such as centrifugal compressors, in order to pump or otherwise move the refrigerant about the chiller.
  • a traditional centrifugal compressor may include a motor which rotates a shaft in order to operate the traditional centrifugal compressor.
  • certain operating and/or ambient conditions may negatively impact the shaft and associated components, reducing an efficiency of the compressor and corresponding chiller. Accordingly, improved compressors for chillers and/or other vapor compression systems may be desired.
  • An embodiment includes a compressor having a shaft, a motor configured to drive the shaft into rotation, and a thrust bearing configured to permit rotation of the shaft and support an axial load of the shaft.
  • the thrust bearing is positioned about the shaft and between the motor and an impeller of the compressor.
  • HVAC&R heating, ventilation, air conditioning, and refrigerant
  • the compressor includes a shaft, a motor configured to drive the shaft into rotation, an impeller coupled to the shaft and configured to be driven into rotation by the shaft, and a thrust bearing configured to permit rotation of the shaft and to support an axial load of the shaft.
  • the thrust bearing is positioned about the shaft and between the motor and the impeller of the compressor.
  • Another embodiment includes a centrifugal compressor having a shaft, a motor configured to drive the shaft into rotation, and a thrust bearing configured to permit rotation of the shaft and to support an axial load of the shaft.
  • the thrust bearing is configured to be disposed within a bearing cavity of the centrifugal compressor, about the shaft, and between the motor and an impeller of the centrifugal compressor.
  • FIG. 1 is a perspective view of a building that may utilize an embodiment of a heating, ventilation, air conditioning, and refrigeration (HVAC&R) system in a commercial setting, in accordance with an aspect of the present disclosure
  • HVAC&R heating, ventilation, air conditioning, and refrigeration
  • FIG. 2 is a perspective view of an embodiment of a vapor compression system, in accordance with an aspect of the present disclosure
  • FIG. 3 is a schematic illustration of an embodiment of the vapor compression system of FIG. 2, in accordance with an aspect of the present disclosure
  • FIG. 4 is a schematic illustration of another embodiment of the vapor compression system of FIG. 2, in accordance with an aspect of the present disclosure
  • FIG. 5 is a cross-sectional side view of an embodiment of a compressor for use in the vapor compression system of FIG. 2, and having a thrust bearing positioned between a motor of the compressor and an impeller of the compressor, in accordance with an aspect of the present disclosure
  • FIG. 6 is a cross-sectional side view of another embodiment of a compressor for use in the vapor compression system of FIG. 2, and having a thrust bearing positioned between a motor of the compressor and an impeller of the compressor, in accordance with an aspect of the present disclosure.
  • a traditional centrifugal compressor may include a motor which rotates a shaft of the compressor in order to operate the traditional centrifugal compressor.
  • certain operating and/or ambient conditions such as certain temperatures and/or pressures, may negatively impact the shaft and associated components, reducing an efficiency of the compressor and corresponding chiller.
  • the shaft of the centrifugal compressor may thermally expand in an axial direction. Shaft growth due to thermal expansion may impact the axial location of the impeller within a diffuser passage of the compressor. Because appropriate axial location of the impeller within the diffuser passage improves efficiency of the compressor, changes to the axial location of the impeller within the diffuser passage due to temperature increase and corresponding thermal expansion of the shaft may reduce efficiency of the compressor.
  • a thrust bearing is positioned on an impeller-side of the motor, and about the shaft.
  • the thrust bearing is positioned between a motor of the compressor and an impeller of the compressor, as opposed to an opposing non-impeller-side of the motor.
  • the thrust bearing is configured to permit rotation of the shaft, and to support an axial load of the shaft against the thrust bearing. In doing so, the axial position of the thrust bearing with respect to axially static components of the compressor does not change.
  • Positioning the thrust bearing on the impeller-side of the motor (i.e., between the motor and the impeller) and about the shaft causes a shorter shaft length between the thrust bearing and the impeller, compared to positioning the thrust bearing on the opposing side (i.e., non-impeller-side) of the motor.
  • axial displacement of the shaft toward the impeller i.e., between the thrust bearing and the impeller
  • temperature changes i.e., thermal expansion
  • axial displacement of the impeller within the diffuser passage is reduced compared to embodiments having no thrust bearing, or a thrust bearing positioned farther away from the impeller. Reducing the axial displacement of the impeller improves efficiency of the compressor, as described above, at least in part because it reduces or negates misalignment of the impeller with respect to the diffuser passage.
  • FIG. 1 is a perspective view of an embodiment of a heating, ventilation, air conditioning, and refrigeration (HVAC&R) system 10 of a building 12 for a typical commercial setting.
  • the HVAC&R system 10 may include a vapor compression system 14 that supplies a chilled liquid, which may be used to cool the building 12.
  • the HVAC&R system 10 may also include a boiler 16 to supply warm liquid to heat the building 12, and an air distribution system which circulates air through the building 12.
  • the air distribution system can also include an air return duct 18, an air supply duct 20, and/or an air handler 22.
  • the air handler 22 may include a heat exchanger that is connected to the boiler 16 and the vapor compression system 14 by conduits 24.
  • the heat exchanger in the air handler 22 may receive either heated liquid from the boiler 16 or chilled liquid from the vapor compression system 14, depending on the mode of operation of the HVAC&R system 10.
  • the HVAC&R system 10 is shown with a separate air handler on each floor of building 12, but in other embodiments, the HVAC&R system 10 may include air handlers 22 and/or other components that may be shared between or among floors.
  • FIGS. 2 and 3 are embodiments of the vapor compression system 14 that can be used in the HVAC&R system 10.
  • the vapor compression system 14 may circulate a refrigerant through a circuit starting with a compressor 32.
  • the circuit may also include a condenser 34, an expansion valve(s) or device(s) 36, and a liquid chiller or an evaporator 38.
  • the vapor compression system 14 may further include a control panel 40 that has an analog to digital (A/D) converter 42, a microprocessor 44, a non-volatile memory 46, and/or an interface board 48.
  • A/D analog to digital
  • HFC hydrofluorocarbon
  • R- 410A R-407, R-l34a
  • HFO hydrofluoro olefin
  • MR ammonia
  • CO2 carbon dioxide
  • R-744 hydrocarbon based refrigerants, water vapor, or any other suitable refrigerant.
  • the vapor compression system 14 may be configured to efficiently utilize refrigerants having a normal boiling point of about 19 degrees Celsius (66 degrees Fahrenheit) at one atmosphere of pressure, also referred to as low pressure refrigerants, versus a medium pressure refrigerant, such as R-l34a.
  • refrigerants having a normal boiling point of about 19 degrees Celsius (66 degrees Fahrenheit) at one atmosphere of pressure also referred to as low pressure refrigerants
  • medium pressure refrigerant such as R-l34a.
  • “normal boiling point” may refer to a boiling point temperature measured at one atmosphere of pressure.
  • the vapor compression system 14 may use one or more of a variable speed drive (VSDs) 52, a motor 50, the compressor 32, the condenser 34, the expansion valve or device 36, and/or the evaporator 38.
  • the motor 50 may drive a shaft of the compressor 32, and may be powered by a variable speed drive (VSD) 52.
  • the VSD 52 receives alternating current (AC) power having a particular fixed line voltage and fixed line frequency from an AC power source, and provides power having a variable voltage and frequency to the motor 50.
  • the motor 50 may be powered directly from an AC or direct current (DC) power source.
  • the motor 50 may include any type of electric motor that can be powered by a VSD or directly from an AC or DC power source, such as a switched reluctance motor, an induction motor, an electronically commutated permanent magnet motor, or another suitable motor.
  • the motor 50, the VSD 52, or both may be separate from the compressor 32, or may be partially or fully integrated with the compressor 32. It should be noted that, in certain embodiments, the motor 50 and/or the VSD 52 may be integral with the compressor 32. For example, the motor 50 may be partially or entirely contained within a casing of the compressor 32.
  • the compressor 32 compresses a refrigerant vapor and delivers the vapor to the condenser 34 through a discharge passage.
  • the compressor 32 may be a centrifugal compressor.
  • the refrigerant vapor delivered by the compressor 32 to the condenser 34 may transfer heat to a cooling fluid (e.g., water or air) in the condenser 34.
  • the refrigerant vapor may condense to a refrigerant liquid in the condenser 34 as a result of thermal heat transfer with the cooling fluid.
  • the liquid refrigerant from the condenser 34 may flow through the expansion device 36 to the evaporator 38.
  • the condenser 34 is water cooled and includes a tube bundle 54 connected to a cooling tower 56, which supplies the cooling fluid to the condenser.
  • the liquid refrigerant delivered to the evaporator 38 may absorb heat from another cooling fluid, which may or may not be the same cooling fluid used in the condenser 34.
  • the liquid refrigerant in the evaporator 38 may undergo a phase change from the liquid refrigerant to a refrigerant vapor.
  • the evaporator 38 may include a tube bundle 58 having a supply line 60S and a return line 60R connected to a cooling load 62.
  • the cooling fluid of the evaporator 38 enters the evaporator 38 via return line 60R and exits the evaporator 38 via supply line 60S.
  • the evaporator 38 may reduce the temperature of the cooling fluid in the tube bundle 58 via thermal heat transfer with the refrigerant.
  • the tube bundle 58 in the evaporator 38 can include a plurality of tubes and/or a plurality of tube bundles. In any case, the vapor refrigerant exits the evaporator 38 and returns to the compressor 32 by a suction line to complete the cycle.
  • FIG. 4 is a schematic of the vapor compression system 14 with an intermediate circuit 64 incorporated between condenser 34 and the expansion device 36.
  • the intermediate circuit 64 may have an inlet line 68 that is directly fluidly connected to the condenser 34.
  • the inlet line 68 may be indirectly fluidly coupled to the condenser 34.
  • the inlet line 68 includes a first expansion device 66 positioned upstream of an intermediate vessel 70.
  • the intermediate vessel 70 may be a flash tank (e.g., a flash intercooler).
  • the intermediate vessel 70 may be configured as a heat exchanger or a“surface economizer.” In the illustrated embodiment of FIG.
  • the intermediate vessel 70 is used as a flash tank, and the first expansion device 66 is configured to lower the pressure of (e.g., expand) the liquid refrigerant received from the condenser 34. During the expansion process, a portion of the liquid may vaporize, and thus, the intermediate vessel 70 may be used to separate the vapor from the liquid received from the first expansion device 66. Additionally, the intermediate vessel 70 may provide for further expansion of the liquid refrigerant because of a pressure drop experienced by the liquid refrigerant when entering the intermediate vessel 70 (e.g., due to a rapid increase in volume experienced when entering the intermediate vessel 70). The vapor in the intermediate vessel 70 may be drawn by the compressor 32 through a suction line 74 of the compressor 32.
  • the vapor in the intermediate vessel may be drawn to an intermediate stage of the compressor 32 (e.g., not the suction stage).
  • the liquid that collects in the intermediate vessel 70 may be at a lower enthalpy than the liquid refrigerant exiting the condenser 34 because of the expansion in the expansion device 66 and/or the intermediate vessel 70.
  • the liquid from intermediate vessel 70 may then flow in line 72 through a second expansion device 36 to the evaporator 38.
  • the compressor 32 in the embodiments illustrated in, and described with respect to, FIGS. 1-4 may include a thrust bearing positioned about a shaft of the compressor 32.
  • the thrust bearing is configured to permit rotation of the shaft, and to support an axial load of the shaft against the thrust bearing. In doing so, the axial distance between the thrust bearing and other axially static components of the compressor 32 does not change.
  • Positioning the thrust bearing on the impeller-side of the motor 50 i.e., between the motor 50 and the impeller of the compressor 32, in accordance with the present disclosure, causes a shorter shaft length between the thrust bearing and the impeller compared to, for example, positioning the thrust bearing on the opposing side (i.e., non-impeller-side) of the motor.
  • FIG. 5 is a side view of an embodiment of the compressor 32 for use in the vapor compression system 14 of FIG. 2.
  • the compressor 32 includes a thrust bearing 100 positioned about a shaft 101 of the compressor 32, positioned between the motor 50 of the compressor 32 and an impeller 102 of the compressor 32 with respect to an axial direction 104 (e.g., along a longitudinal axis 115 of the compressor 32).
  • the thrust bearing 100, the shaft 101, the impeller 102, the motor 50, and other features of the compressor 32 may be contained within a casing 103 of the compressor 32.
  • the motor 50 may be integral with the compressor 32.
  • the motor 50 may be configured to rotate the shaft 101 to cause compression of refrigerant passing through the compressor 32 (and to move the refrigerant through a corresponding chiller or vapor compression system).
  • the shaft 101 may cause rotation of the impeller 102, which includes a set of vanes and/or blades that gradually increases the energy of the refrigerant and directs the refrigerant toward a diffuser passage 112 of the compressor 32.
  • the diffuser passage 112 of the compressor 32 may include a vane, vaneless, or variable geometry diffuser, which operates to diffuse the high-energy refrigerant gas. That is, the diffuser passage 112 and corresponding diffuser may convert the kinetic energy of the refrigerant gas into pressure by gradually reducing a velocity thereof.
  • the refrigerant gas may then flow through a collector 113 downstream of the diffuser passage 112.
  • the impeller 102 may be axially positioned (e.g., with respect to direction 104 along the longitudinal axis 115) such that the impeller 102 guides the refrigerant toward appropriate locations of the diffuser passage 112 and corresponding diffuser.
  • the shaft 101 may thermally expand along an axial direction 104 (e.g., along the longitudinal axis 115 of the compressor 32).
  • the thrust bearing 100 is configured to permit rotation of the shaft 101 while supporting an axial load of the shaft 101. In other words, the thrust bearing 100 maintains its axial position with respect to, for example, the motor 50.
  • the thrust bearing 100 is positioned between the motor 50 of the compressor 32 and the impeller 102 of the compressor 32.
  • the thrust bearing 100 is positioned on an impeller-side 106 of the motor 50, as opposed to a non-impeller-side 108 of the motor 50.
  • a shaft length 110 between the thrust bearing 100 and the impeller 102 is less than if the thrust bearing 100 were disposed on the non-impeller-side 108 of the motor 50.
  • the available shaft length 110 that can thermally expand between the axially static thrust bearing 100 and the impeller 102 is small compared to embodiments having a thrust bearing positioned farther away from the impeller 102.
  • an additional shaft length 111 extending from the thrust bearing 100, through the motor 50, and through the non- impeller-side 108 of the motor 50 is significantly larger than the illustrated shaft length 110 between the thrust bearing 100 and the impeller 102.
  • the disclosed thrust bearing 100 and corresponding axial location along the shaft 101 improves efficiency of the compressor 32.
  • the compressors 32 of FIGS. 5 and 6 may be centrifugal compressors, hermetic compressors, overhung compressors, or any combination thereof (e.g., hermetic overhung centrifugal compressor).
  • the thrust bearing 100 is a lubricated hydrodynamic bearing
  • the thrust bearing 100 is a magnetic bearing.
  • the thrust bearing 100 may be positioned within a cavity 105 (e.g., bearing cavity) formed within the compressor 32 (e.g., formed inside the casing 103 and/or with respect to other features of the compressor 32).
  • the cavity 105 may be configured (e.g., sized and/or shaped) to receive the thrust bearing 100, and the thrust bearing 100 may be configured (e.g., sized and/or shaped) to be disposed in the cavity 105.
  • FIG. 6 is cross-sectional side view of another embodiment of the compressor 32 for use in the vapor compression system 14 of FIG. 2. Similar to the embodiment illustrated in FIG. 5, the compressor 32 illustrated in FIG. 6 includes the thrust bearing 100 positioned about the shaft 101 and on the impeller-side 106 of the motor 50. Accordingly, the shaft length 110 between the thrust bearing 100 and the impeller 102 is reduced compared to embodiments having no thrust bearing or a thrust bearing positioned farther from the impeller (e.g., on the non-impeller-side 108 of the motor 50).
  • the thrust bearing 100 is a lubricated hydrodynamic bearing
  • the thrust bearing 100 is a magnetic bearing
  • any suitable thrust bearing may be utilized in FIG. 5 and in FIG. 6.
  • the above-described technical effects which relate to a position of the thrust bearing 100 and corresponding reduction of displacement of the impeller 102 with respect to the diffuser passage 112 may be applicable in embodiments utilizing magnetic bearings, anti-friction bearings (e.g., oil or refrigerant lubricated anti-friction bearings such as roller bearings or ball bearings), lubricated hydrodynamic bearings, and any other suitable thrust bearings.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Electromagnetism (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

Un compresseur (32) comprend un arbre (101), un moteur (50) configuré pour entraîner l'arbre (101) en rotation, et un palier de butée (100) configuré pour permettre la rotation de l'arbre (101) et supporter une charge axiale de l'arbre (101). Le palier de butée (100) est positionné autour de l'arbre (101) et entre le moteur (50) et une roue (102) du compresseur (32).
PCT/US2018/067710 2017-12-29 2018-12-27 Placement de palier de butée pour compresseur WO2019133725A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US201762611722P 2017-12-29 2017-12-29
US62/611,722 2017-12-29
US16/232,738 2018-12-26
US16/232,738 US20190203730A1 (en) 2017-12-29 2018-12-26 Thrust bearing placement for compressor

Publications (1)

Publication Number Publication Date
WO2019133725A1 true WO2019133725A1 (fr) 2019-07-04

Family

ID=67057644

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2018/067710 WO2019133725A1 (fr) 2017-12-29 2018-12-27 Placement de palier de butée pour compresseur

Country Status (3)

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US (1) US20190203730A1 (fr)
TW (1) TW201930725A (fr)
WO (1) WO2019133725A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012166325A1 (fr) * 2011-05-31 2012-12-06 Carrier Corporation Atténuation du jeu dans un compresseur
EP2677176A1 (fr) * 2012-06-22 2013-12-25 Skf Magnetic Mechatronics Compresseur centrifuge électrique compact
EP2962616A1 (fr) * 2014-07-01 2016-01-06 LG Electronics Inc. Pompe et lave-vaisselle équipé d'une pompe

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5660481A (en) * 1987-05-29 1997-08-26 Ide; Russell D. Hydrodynamic bearings having beam mounted bearing pads and sealed bearing assemblies including the same
IL109967A (en) * 1993-06-15 1997-07-13 Multistack Int Ltd Compressor
US7704056B2 (en) * 2007-02-21 2010-04-27 Honeywell International Inc. Two-stage vapor cycle compressor
WO2009088846A1 (fr) * 2007-12-31 2009-07-16 Johnson Controls Technology Company Procédé et système de refroidissement de rotor
FR2932530B1 (fr) * 2008-06-17 2011-07-01 Snecma Turbomachine a systeme de maintien en position longue duree
ITFI20130204A1 (it) * 2013-09-03 2015-03-04 Nuovo Pignone Srl "fan-cooled electrical machine with axial thrust compensation"
JP6223859B2 (ja) * 2014-02-24 2017-11-01 三菱重工業株式会社 過給機及びモータ冷却方法
JP2016173085A (ja) * 2015-03-18 2016-09-29 三菱重工業株式会社 圧縮機システム
US20170002825A1 (en) * 2015-03-27 2017-01-05 Dresser-Rand Company Balance piston with a sealing member
JP6398897B2 (ja) * 2015-07-23 2018-10-03 株式会社豊田自動織機 遠心圧縮機

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012166325A1 (fr) * 2011-05-31 2012-12-06 Carrier Corporation Atténuation du jeu dans un compresseur
EP2677176A1 (fr) * 2012-06-22 2013-12-25 Skf Magnetic Mechatronics Compresseur centrifuge électrique compact
EP2962616A1 (fr) * 2014-07-01 2016-01-06 LG Electronics Inc. Pompe et lave-vaisselle équipé d'une pompe

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TW201930725A (zh) 2019-08-01
US20190203730A1 (en) 2019-07-04

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