WO2012166858A1 - Compresseur centrifuge économique - Google Patents

Compresseur centrifuge économique Download PDF

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Publication number
WO2012166858A1
WO2012166858A1 PCT/US2012/040114 US2012040114W WO2012166858A1 WO 2012166858 A1 WO2012166858 A1 WO 2012166858A1 US 2012040114 W US2012040114 W US 2012040114W WO 2012166858 A1 WO2012166858 A1 WO 2012166858A1
Authority
WO
WIPO (PCT)
Prior art keywords
fluid
economizer
heat exchanger
compressor
flow
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.)
Ceased
Application number
PCT/US2012/040114
Other languages
English (en)
Inventor
Vishnu M. Sishtla
Joost Brasz
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.)
Carrier Corp
Original Assignee
Carrier Corp
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 Carrier Corp filed Critical Carrier Corp
Priority to CN201280026288.9A priority Critical patent/CN103562561A/zh
Priority to US14/006,326 priority patent/US20140182317A1/en
Publication of WO2012166858A1 publication Critical patent/WO2012166858A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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
    • F04D29/40—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
    • F04D29/40—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
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • 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
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • F04D27/0207—Surge control by bleeding, bypassing or recycling fluids
    • F04D27/0238—Details or means for fluid reinjection
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F25B1/053—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of turbine type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/52—Outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—Component parts or details not otherwise provided for in this subclass
    • F25B2400/13—Economisers

Definitions

  • the disclosure relates to compressors. More particularly, the disclosure relates to electric motor-driven hermetic or semi-hermetic compressors.
  • An exemplary liquid chiller uses a hermetic centrifugal compressor.
  • the exemplary unit comprises a standalone combination of the compressor, the cooler unit, the chiller unit, the expansion device, and various additional components.
  • the exemplary compressor includes a transmission intervening between the motor rotor and the impeller to drive the impeller at a faster speed than the motor.
  • Chiller centrifugal compressors include both two-stage models and single-stage models.
  • US5145317, US5445496, US6547520, and US6814540 disclose single stage models.
  • the interstage of a two-stage model may be communicated with an economizer port.
  • An economized single stage compressor has been proposed wherein refrigerant is injected along the impeller.
  • One aspect of the disclosure involves a compressor having a housing assembly with a suction port, a discharge port, and an economizer port.
  • An impeller is mounted to be driven in at least a first condition so as to draw a main flow of fluid through the suction port and discharge the fluid from the discharge port.
  • a diffuser has a plurality of diffuser passages. Each diffuser passage has an inlet positioned to receive fluid from the impeller and an outlet downstream of the inlet in the first condition.
  • One or more passages are positioned to draw an economizer flow of fluid from the economizer port and deliver the economizer flow downstream of the impeller inlet but upstream of the diffuser passage outlets.
  • FIG. 1 is a partially schematic view of a chiller system.
  • FIG. 2 is a longitudinal sectional view of a compressor of the chiller system.
  • FIG. 3 is an enlarged view of an upstream region of the compressor of FIG. 2.
  • FIG. 4 is a partial transverse cutaway view of a diffuser of the compressor of FIG. 3, taken alon g line 4-4.
  • FIG. 5 is an enlarged longitudinal sectional view of an upstream region of an alternate compressor.
  • FIG. 6 is a longitudinal sectional view of an alternative compressor of the chiller system.
  • FIG. 7 is a partial enlarged view of an upstream region of the compressor of FIG. 6.
  • FIG. 8 is a pressure-enthalpy diagram for the compressor of FIG. 2.
  • FIG. 9 is an enlarged longitudinal sectional view of an upstream region of an alternate compressor.
  • FIG. 1 shows a vapor compression system 20.
  • the exemplary vapor compression system 20 is a chiller system.
  • the system 20 includes a compressor 22 having a suction port (inlet) 24 and a discharge port (outlet) 26.
  • the system further includes a first heat exchanger 28 in a normal operating mode being a heat rejection heat exchanger (e.g., a gas cooler or condenser).
  • the heat exchanger 28 is a refrigerant- water heat exchanger in a condenser unit 29 where the refrigerant is cooled by a water (or other heat transfer fluid) flow from an external source (not shown).
  • the system further includes a second heat exchanger 30 (in the normal mode a heat absorption heat exchanger or evaporator).
  • the heat exchanger 30 is a refrigerant- water heat exchanger for chilling a chilled water flow within a chiller (or cooler) unit 31.
  • An expansion device 32 is downstream of the heat rejection heat exchanger and upstream of the heat absorption heat exchanger along the normal mode refrigerant flowpath 34 (the flowpath being partially surrounded by associated piping, etc.).
  • the exemplary expansion device 32 is formed by a distributor of the cooler unit 31.
  • a flash tank economizer 40 is located along the flowpath 34 between a refrigerant outlet 42 of the condenser and a refrigerant inlet 44 of the cooler.
  • the economizer has a primary refrigerant inlet 46, a primary refrigerant outlet 48, and a secondary refrigerant outlet 50.
  • a liquid refrigerant accumulation is maintained in the tank 52 via a float valve 54 controlling flow through the outlet 48.
  • An economizer flowpath branch 56 extends from the secondary outlet 50 to an economizer port 58 of the compressor.
  • FIG. 1 further shows a refrigerant inlet 60 of the condenser, a refrigerant outlet 62 of the cooler, and a float valve 64 of the condenser controlling flow through the outlet 42.
  • FIG. 1 further shows conduits/flowpaths for various equipment cooling functions.
  • an equipment cooling flowpath/branch 80 branches off from the main flowpath 34 at the float valve sump, upstream of the float valve.
  • the flowpath 80 further branches into three branches or sub-branches 82, 84, and 86.
  • the exemplary branch 82 passes through an oil cooler 90 to cool compressor oil from a reservoir (not shown) located in compressor 22.
  • the branch 84 passes through a cold plate 92 of a variable frequency drive (VFD; not shown) of the compressor motor.
  • VFD variable frequency drive
  • the branches 84 and 82 merge into a branch 83 which enters a secondary inlet 94 of the economizer.
  • the branch 86 passes to a motor compartment inlet 100 of the compressor housing and cools the motor, thereafter exiting a motor compartment outlet 102 and entering a secondary inlet 104 of the cooler downstream of the distributor.
  • FIG. 1 further shows various isolation and/or control valves. These include: a compressor discharge isolation valve 120 in the compressor discharge line along the flowpath 34 between the discharge port/outlet 26 and the condenser inlet 60; a condenser isolation valve 122 along the flowpath 34 downstream of the condenser outlet 42 and upstream of the economizer inlet 46; a cooler isolation valve 124 along the flowpath 34 downstream of the economizer outlet 48 and upstream of the cooler inlet 44; an economizer isolation valve 126 along the branch 56 between the economizer secondary outlet 50 and the compressor economizer port 58; a valve in the branch 86; a cooling isolation valve 128 in the branch 80 (capable of interrupting flow through all three branches 82, 84, and 86); and an oil/VFD cooler isolation valve 130 in the branch 83 and a valve 131 in the branch 86 for isolating the oil cooler 90 and cold plate 92.
  • a compressor discharge isolation valve 120 in the compressor discharge line along the flowpath 34
  • FIG. 1 further shows a controller 132 (e.g., a microprocessor-based controller or other such controller) coupled to the various sensors, user input devices, and controllable system components to control operation in accordance with pre-programmed methods.
  • a controller 132 e.g., a microprocessor-based controller or other such controller
  • FIG. 1 further shows a main tube bundle 140 and sub-cooler tube bundle 142 of the heat rejection heat exchanger which carry heat transfer fluid (e.g., environmental water or water to be heated for use).
  • FIG. 1 further shows a tube bundle 144 of the heat absorption heat exchanger (e.g., carrying water, brine, or other heat transfer fluid to be chilled).
  • An exemplary compressor is a centrifugal compressor having a housing assembly (housing) 150.
  • the housing assembly contains an electric motor 152 and an impeller 144 drivable by the electric motor in the first mode to draw fluid (refrigerant) in through the suction port 24, compress the fluid, and discharge the fluid from the discharge port.
  • the exemplary impeller is driven indirectly by the motor via a transmission 156.
  • the housing defines a motor compartment 160 containing a stator 162 of the motor within the compartment.
  • a rotor 164 of the motor is partially within the stator and is mounted for rotation about a rotor axis 500.
  • the exemplary mounting is via one or more bearing systems 166, mounting a shaft 170 of the rotor to the housing assembly.
  • the exemplary impeller 154 is mounted to its own shaft 172 to rotate about an axis 502.
  • An exemplary bearing system 174 mounts an intermediate portion of the shaft 172 to an intermediate wall 178 of the housing assembly.
  • FIG. 2 further shows the compressor inlet 24 and outlet 26.
  • the inlet 24 is at the upstream end of a suction housing member 200 of the housing assembly.
  • the suction housing member carries a circumferential array of inlet guide vanes 202 which may be articulated (e.g., rotated about respective axes via an actuator not shown) to control the inlet (suction) flow.
  • the flowpath extends downstream to the upstream end or tip 204 of the impeller 154.
  • the impeller has a generally downstream outwardly flaring body 206 bearing blades 208. The blade tips fall along a shroud 210 of the housing assembly extending downstream from the suction housing 200.
  • the impeller and shroud thus define a generally axial inlet 212 and a radial outlet 214.
  • the outlet 214 of the impeller is surrounded by a diffuser 220.
  • the diffuser has a circumferential array of passageways 222 extending from inlets 224 to outlets 226.
  • Each passageway is a partial tangential orientation and has a cross-sectional area increasing from upstream/inboard to downstream/outboard.
  • the outlets are along a discharge plenum 228.
  • FIG. 3 further shows the economizer port 58.
  • the exemplary port 58 is along a suction housing chamber 230 radially outboard of an upstream portion of the shroud.
  • the economizer flowpath thus passes through a conduit (e.g., tube) 231 within this chamber and through a port 232 in the diffuser.
  • the economizer flowpath then passes through one or more bores 236 to intersect with the diffuser passageways 222.
  • An exemplary intersection is just downstream of the inlets 224.
  • FIG. 4 further shows the intersection 240 of the bores 236 and the passageways.
  • There may be plural such ports and/or conduits e.g., a circumferential array fed by branches of the conduit 231) sufficient to provide a desired flow rate and distribution. For example, a sufficient number of bores 236 of sufficient diameter may be provided to
  • the port 58, chamber conduit 231 , and bores 236 thus define the one or more passages positioned to draw the economizer flow from the economizer port and deliver the economizer flow downstream of the impeller inlet but upstream of the diffuser passage outlets.
  • the economizer flow is delivered downstream of the impeller outlets, more particularly, at or slightly downstream of the diffuser passageway inlets.
  • FIG. 5 shows an alternate compressor 260 wherein, rather than penetrating the diffuser, the economizer flowpath extends to a gap 262 between the diffuser and the impeller.
  • the flowpath may further pass through a gap 264 between the impeller shroud and the diffuser.
  • the exemplary economizer flowpath passes through a mounting flange 266 of the shroud extending radially outward and mating with the diffuser.
  • the exemplary economizer flowpath is defined by one or more conduits 268 or branches thereof extending from the economizer port 58 to one or more associated apertures 270 in the flange.
  • the economizer flowpath and main/primary flowpath may thus merge at the intersection/gap 262.
  • FIG. 6 shows an alternate compressor 300 having a variable diffuser 302.
  • the diffuser 302 comprises a fixed outer member (outer diffuser ring) 304 and a movable inner member (inner diffuser ring) 306 (e.g., rotatable about the axis 502).
  • the inner diffuser ring may be rotated relative to the outer diffuser ring so as to bring inboard/upstream portions 308 (FIG. 7) of the passageways (in the inner diffuser ring) into and out of registration with
  • the exemplary economizer passage and flowpath pass from the economizer port 58 through a conduit 320 (the conduit 320 passing through the suction housing chamber 230). A downstream end of the conduit 320 is mounted in a bore 321 in an outboard flange 322 of the shroud. As the embodiment above, there may be multiple such conduits 320 or branches thereof and multiple such bores to provide a desired economizer flow.
  • the economizer flowpath After exiting the bores 320, the economizer flowpath passes into a shroud chamber 330 along an outboard surface of a downstream portion of the shroud and inboard of an inner/ID surface of the inner diffuser ring. There may be a small radial clearance 332 between the shroud and the diffuser ring through which the economizer flowpath may pass to merge with the main flowpath at the interface of the impeller and diffuser ring.
  • FIG. 8 is a pressure-enthalpy diagram for the system of FIG. 1.
  • the exact location of the intersection of the economizer flowpath and the main flowpath may be chosen based upon anticipated system conditions. As noted above, a convenient location is exactly between the impeller outlet and diffuser inlet. However, locations more downstream within the diffuser are possible (e.g., between 0% and 70% of a length from the diffuser inlet to the diffuser outlet, more narrowly, 0-50% or 10-50%).
  • FIG. 9 shows a compressor 400 having a vaneless diffuser 402 having an annular passageway 403.
  • the passageway 403 has an inboard inlet 404 and an outboard outlet 406 to a discharge plenum 408.
  • the economizer conduit has an outlet 410 of the economizer conduit 412 along the diffuser intermediate the inlet 404 and outlet 406 (but, in the exemplary embodiment, much closer to the inlet 404).

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne un compresseur (22 ; 260 ; 300 ; 400) qui possède un ensemble corps (140) ayant un orifice d'aspiration (24), un orifice de refoulement (26) et un orifice d'économiseur (58). Un rotor (154) est monté de façon à être entraîné dans au moins un premier état de manière à aspirer un flux principal de fluide à travers l'orifice d'aspiration et à refouler le fluide par l'orifice de refoulement. Un diffuseur (220 ; 302 ; 402) possède une pluralité de passages de diffuseur (222 ; 310 ; 308 ; 403). Chaque passage de diffuseur présente une entrée (224) positionnée pour recevoir un fluide du rotor et une sortie (220) en aval de l'entrée dans le premier état. Un ou plusieurs passages (230, 231, 232, 234, 236, 268 ; 320, 330, 332 ; 412) sont positionnés pour attirer un flux de fluide d'économiseur à travers l'orifice d'économiseur et pour débiter le flux d'économiseur en aval de l'entrée du rotor (212) mais en amont des sorties du passage de diffuseur (226).
PCT/US2012/040114 2011-06-01 2012-05-31 Compresseur centrifuge économique Ceased WO2012166858A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201280026288.9A CN103562561A (zh) 2011-06-01 2012-05-31 经济化离心压缩机
US14/006,326 US20140182317A1 (en) 2011-06-01 2012-05-31 Economized Centrifugal Compressor

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201161492109P 2011-06-01 2011-06-01
US61/492,109 2011-06-01

Publications (1)

Publication Number Publication Date
WO2012166858A1 true WO2012166858A1 (fr) 2012-12-06

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PCT/US2012/040114 Ceased WO2012166858A1 (fr) 2011-06-01 2012-05-31 Compresseur centrifuge économique

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US (1) US20140182317A1 (fr)
CN (1) CN103562561A (fr)
WO (1) WO2012166858A1 (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2905477A1 (fr) * 2014-02-10 2015-08-12 Pratt & Whitney Canada Corp. Diffuseur de compresseur centrifuge et son procédé de commande
WO2015122991A3 (fr) * 2014-02-17 2015-11-26 Carrier Corporation Dérivation de gaz chauds pour compresseur à deux étages
EP3006861A4 (fr) * 2013-06-04 2017-03-29 Daikin Industries, Ltd. Réfrigérateur à turbo
WO2017123598A1 (fr) * 2016-01-12 2017-07-20 Daikin Applied Americas Inc. Compresseur centrifuge à injection de liquide
US9926942B2 (en) 2015-10-27 2018-03-27 Pratt & Whitney Canada Corp. Diffuser pipe with vortex generators
US10570925B2 (en) 2015-10-27 2020-02-25 Pratt & Whitney Canada Corp. Diffuser pipe with splitter vane
US11378005B1 (en) 2020-12-17 2022-07-05 Pratt & Whitney Canada Corp. Compressor diffuser and diffuser pipes therefor
US20220290692A1 (en) * 2021-03-10 2022-09-15 Daikin Industries, Ltd. Centrifugal compressor with liquid injection

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3325816B1 (fr) 2015-07-22 2019-08-28 Carrier Corporation Anneau de restriction de diffuseur
EP3997343B1 (fr) 2019-07-01 2023-08-09 Carrier Corporation Protection contre les surtensions pour compresseur à plusieurs étages
TW202212694A (zh) * 2020-07-30 2022-04-01 美商江森自控泰科知識產權控股有限責任合夥公司 用於引導壓縮機中的流體流之系統及方法

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1035669B (de) * 1954-08-09 1958-08-07 Frantisek Wergner Verfahren zum Betrieb einer Kompressor-Kuehlanlage mit mindestens zweistufiger Kompression eines in der Anlage umlaufenden Kaeltemittels sowie Kompressor-Kuehlanlage zur Durchfuehrung des Verfahrens
US3226940A (en) * 1963-12-12 1966-01-04 Worthington Corp Single stage centrifugal compressor refrigeration system
US4691533A (en) * 1985-09-27 1987-09-08 Bernard Zimmern Refrigeration system with a centrifugal economizer
US5145317A (en) 1991-08-01 1992-09-08 Carrier Corporation Centrifugal compressor with high efficiency and wide operating range
US5445496A (en) 1990-10-30 1995-08-29 Carrier Corporation Centifugal compressor with pipe diffuser and collector
US6547520B2 (en) 2001-05-24 2003-04-15 Carrier Corporation Rotating vane diffuser for a centrifugal compressor
US6814540B2 (en) 2002-10-22 2004-11-09 Carrier Corporation Rotating vane diffuser for a centrifugal compressor

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5434161A (en) * 1977-08-20 1979-03-13 Ebara Corp Turbo refrigerator
AU8099982A (en) * 1981-03-19 1982-09-23 Mcquay-Perfex, Inc. Centrifugal refrigeration compressor
JPS58214697A (ja) * 1982-06-08 1983-12-13 Ebara Corp 遠心式ヒ−トポンプ
US4611969A (en) * 1985-08-19 1986-09-16 Carrier Corporation Calibrating apparatus and method for a movable diffuser wall in a centrifugal compressor
US4997340A (en) * 1989-09-25 1991-03-05 Carrier Corporation Balance piston and seal arrangement
US5807071A (en) * 1996-06-07 1998-09-15 Brasz; Joost J. Variable pipe diffuser for centrifugal compressor
US8235648B2 (en) * 2008-09-26 2012-08-07 Pratt & Whitney Canada Corp. Diffuser with enhanced surge margin

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1035669B (de) * 1954-08-09 1958-08-07 Frantisek Wergner Verfahren zum Betrieb einer Kompressor-Kuehlanlage mit mindestens zweistufiger Kompression eines in der Anlage umlaufenden Kaeltemittels sowie Kompressor-Kuehlanlage zur Durchfuehrung des Verfahrens
US3226940A (en) * 1963-12-12 1966-01-04 Worthington Corp Single stage centrifugal compressor refrigeration system
US4691533A (en) * 1985-09-27 1987-09-08 Bernard Zimmern Refrigeration system with a centrifugal economizer
US5445496A (en) 1990-10-30 1995-08-29 Carrier Corporation Centifugal compressor with pipe diffuser and collector
US5145317A (en) 1991-08-01 1992-09-08 Carrier Corporation Centrifugal compressor with high efficiency and wide operating range
US6547520B2 (en) 2001-05-24 2003-04-15 Carrier Corporation Rotating vane diffuser for a centrifugal compressor
US6814540B2 (en) 2002-10-22 2004-11-09 Carrier Corporation Rotating vane diffuser for a centrifugal compressor

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3006861A4 (fr) * 2013-06-04 2017-03-29 Daikin Industries, Ltd. Réfrigérateur à turbo
EP2905477A1 (fr) * 2014-02-10 2015-08-12 Pratt & Whitney Canada Corp. Diffuseur de compresseur centrifuge et son procédé de commande
US9803652B2 (en) 2014-02-10 2017-10-31 Pratt & Whitney Canada Corp. Centrifugal compressor diffuser and method for controlling same
US10267539B2 (en) 2014-02-17 2019-04-23 Carrier Corporation Hot gas bypass for two-stage compressor
WO2015122991A3 (fr) * 2014-02-17 2015-11-26 Carrier Corporation Dérivation de gaz chauds pour compresseur à deux étages
US10502231B2 (en) 2015-10-27 2019-12-10 Pratt & Whitney Canada Corp. Diffuser pipe with vortex generators
US9926942B2 (en) 2015-10-27 2018-03-27 Pratt & Whitney Canada Corp. Diffuser pipe with vortex generators
US10570925B2 (en) 2015-10-27 2020-02-25 Pratt & Whitney Canada Corp. Diffuser pipe with splitter vane
US11215196B2 (en) 2015-10-27 2022-01-04 Pratt & Whitney Canada Corp. Diffuser pipe with splitter vane
JP2019502054A (ja) * 2016-01-12 2019-01-24 ダイキン アプライド アメリカズ インコーポレィティッド 液インジェクションが行われる遠心圧縮機
WO2017123598A1 (fr) * 2016-01-12 2017-07-20 Daikin Applied Americas Inc. Compresseur centrifuge à injection de liquide
US10563673B2 (en) 2016-01-12 2020-02-18 Daikin Applied Americas Inc. Centrifugal compressor with liquid injection
US11378005B1 (en) 2020-12-17 2022-07-05 Pratt & Whitney Canada Corp. Compressor diffuser and diffuser pipes therefor
US20220290692A1 (en) * 2021-03-10 2022-09-15 Daikin Industries, Ltd. Centrifugal compressor with liquid injection
US12158165B2 (en) * 2021-03-10 2024-12-03 Daikin Industries, Ltd. Centrifugal compressor with liquid injection
US20250052258A1 (en) * 2021-03-10 2025-02-13 Daikin Industries, Ltd. Centrifugal compressor with liquid injection

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US20140182317A1 (en) 2014-07-03

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