US3362625A - Centrifugal gas compressor - Google Patents

Centrifugal gas compressor Download PDF

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Publication number
US3362625A
US3362625A US577447A US57744766A US3362625A US 3362625 A US3362625 A US 3362625A US 577447 A US577447 A US 577447A US 57744766 A US57744766 A US 57744766A US 3362625 A US3362625 A US 3362625A
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Prior art keywords
compressor
diffuser
control member
guide vanes
centrifugal
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Expired - Lifetime
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US577447A
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James W Endress
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Carrier Corp
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Carrier Corp
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Priority to US577447A priority Critical patent/US3362625A/en
Priority to GB35032/67A priority patent/GB1190796A/en
Priority to JP42051643A priority patent/JPS5010001B1/ja
Priority to FR1549304D priority patent/FR1549304A/fr
Priority to NL6712176A priority patent/NL6712176A/xx
Priority to DE19671628232 priority patent/DE1628232C/en
Application granted granted Critical
Publication of US3362625A publication Critical patent/US3362625A/en
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    • 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
    • F04D29/46—Fluid-guiding means, e.g. diffusers adjustable
    • F04D29/462—Fluid-guiding means, e.g. diffusers adjustable 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
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • F04D27/0246—Surge control by varying geometry within the pumps, e.g. by adjusting vanes
    • 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
    • F04D27/0253—Surge control by throttling
    • 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
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4213—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps suction ports
    • 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
    • F04D29/46—Fluid-guiding means, e.g. diffusers adjustable
    • F04D29/462—Fluid-guiding means, e.g. diffusers adjustable especially adapted for elastic fluid pumps
    • F04D29/464—Fluid-guiding means, e.g. diffusers adjustable especially adapted for elastic fluid pumps adjusting flow cross-section, otherwise than by using adjustable stator blades
    • 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
    • F05D2250/51—Inlet
    • 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

Definitions

  • This invention relates to gas compression equipment. More particularly, this invention relates to centrifugal gas compressors. Still more particularly, this invention relates to centrifugal gas compressors subjected to large load variations.
  • the objects of this invention are attained by providing a centrifugal gas compressor with inlet guide vanes and diffuser restriction means.
  • An annular control member arranged for movement in a circular path, simultaneously effects the position of the inlet guide vanes and the diffuser restriction means to provide peak efiiciency at any flow rate.
  • FIGURE 1 is an elevational view, partly in section of a portion of a centrifugal compressor including the impeller, inlet guide vanes, and diffuser passage, the compressor incorporating my invention.
  • FIGURE 2 is a view taken along line II-II of FIG- URE 1.
  • FIGURE 3 is a fragmentary elevational view, partly in section of the compressor in FIGURE 1, further illustrating the guide vane and diffuser restriction actuator means of my invention.
  • a gas compressor 1 of the well-known centrifugal type wherein gas to be compressed is induced to flow in an axial direction into a vaned impeller connected to a suitable drive for imparting rotary motion thereto.
  • the compressor includes a housing 2 with inlet passage 3 and diffuser passage 5. Only a portion of the housing is shown, it being understood that such a construction is conventional in equipment of the kind under consideration.
  • An impeller 7, affixed to shaft 9 by nut 11 is provided in housing 2 between the inlet passage 3 and diffuser passage 5.
  • Inlet guide vanes 13 journaled for rotation in housing 2 are positioned about the inlet passage to control the direction and quantity of gas flow therethrough.
  • An annular control member 15 is mounted on balls 17 in stationary race 19 for movement in a circular path.
  • a plurality of cam tracks 21 equally spaced circumferentially of annular control member 15 are provided for mating engagement with cam followers 23.
  • Cam followers 23 are comprised of rollers 25 bolted on push rods 27.
  • Push rods 27 are bolted to diffuser restriction ring 29 so that rotation of annual control member 15 will effect axial movement of diffuser restriction ring 29 within diffuser passage 5, note the position indicated in dotted lines, said movement conforming to the shape and size of the tracks 21.
  • Arms 31, on guide vanes 13 are connected to annular control member 15 by links 33 so that rotation of annular control member 15 will also effect rotation of guide vanes 13.
  • a control rod 35 is mounted for rotation about its longitudinal axis to rotate annular control member 15 by means of links 37 and 39 pivotally mounted therehetween.
  • the control rod 35 can be rotated by any well-known means (not shown) such as electric, pneumatic or hydraulic positioners responsive to an operating condition of the compressor or its associated equipment which is indicative of the load on the compressr.
  • the positioning means could be responsive to the temperature of the chilled water leaving the machine, this temperature being related to the quantity of refrigerant being lifted from the low side to the high side of the machine by the compressor. If the compressor were being used to compress air, the positioning means could be responsive to ambient temperature since this is an indication of the air density and therefore the quantity of air being compressed.
  • cam tracks 21 have a specialized configuration.
  • the track is so designed that rotation of annular control member 15 will rotate the guide vanes from full open position to a 60% closed position without restricting diffuser passage 5. If a reduction in flow greater than that caused by the guide vanes in the 60% closed position is desired, further rotation of annular control member 15 will simultaneously move guide vanes 13 between 60% closed and closed and move diffuser restriction ring to provide a diffuser capacity between and 5% of maximum. If a greater reduction than this is desired, further rotation of annular control member 15 will hold the diffuser restriction ring 3 in the 5% diffuser capacity position and move guide vanes 13 between 85% and 100% closed.
  • a centrifugal gas compressor comprising, a housing having an inlet passage and a diffuser passage formed therein, an impeller mounted in said housing between the inlet and diffuser thereof, a plurality of guide vanes pivotally mounted in the housing to vary the quantity of gas flowing through the inlet passage, diffuser restriction means including an annular diffuser member mounted for axial movement across the diffuser passage to restrict fiow of gas therethrough, actuator means including an annular control member arranged for movement in a circular path about the inlet passage connected to said guide vanes and regulating means effective in response to and operable only after a predetermining movement of the annular control member and pivoting of said guide vanes for axially positioning said annular diffuser member in response to further movement of said annular control member.
  • said regulating means includes a plurality of cam followers attached to said diffuser restriction means, said annular control member having a plurality of cam tracks formed therein for engagement by said cam followers to move said diffuser restriction means in response to the circular movement of said annular control member.
  • said actuator means further includes guide vane linkage between said annular control member and said guide vanes, said guide vane linkage means comprising arms, affixed to said guide vanes for rotation therewith, and, linking rods, pivotally connected to said annular control member and said arms to rotate said guide vanes when said annular control member is rotated.
  • said actuator means further includes a control rod mounted in said housing for rotation therein, and, control rodlinkage means, operably associated with said annular control member so that rotation of said control rod effects rotation of said annular control member.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Control Of Positive-Displacement Air Blowers (AREA)

Description

Jan. 9, 1968 Filed Sept. 6, 1966 2 Shets-Sheet 1 INVENTOR JAMES w.- ENDRESS..
ATTORNEY.
Jan. 9, 1968 J. w. ENDRESS 3,362,625
' CENTRIFUGAL GAS COMPRESSOR Filed Sept. 6. 1966 2 Sheets-Sheet FIG. 3
t--- l JJ JJ' jl l 2; v INVENTQR.
-. JAMES W. ENDRESS.
ATTORNEY.
United States Patent 3,362,625 CENTRIFUGAL GAS COMPRESSOR James W. Endress, Syracuse, N.Y., assignor to Carrier Corporation, Syracuse, N.Y., a corporation of Delaware Filed Sept. 6, 1966, Ser. No. 577,447 4 Claims. (Cl. 230-114) ABSTRACT OF THE DISCLOSURE A centrifugal compressor capable of stable operation under low volumetric flow rates. An annular ring, rotatable about the axis of the compressor is operably connected to inlet guide vanes and a diffuser restriction ring to provide programmed restriction of the inlet and diffuser passages in relation to the compressor loading.
This invention relates to gas compression equipment. More particularly, this invention relates to centrifugal gas compressors. Still more particularly, this invention relates to centrifugal gas compressors subjected to large load variations.
One of the major problems arising in the use of centrifugal gas compressors for applications where the compression load varies over a wide range is flow stabilization through the compressor. The compressor inlet, impeller and diffuser passage must be sized to provide for the maximum volumetric flow rate desired. When there is a low volumetric flow rate through such a compressor, the flow becomes unstable. As the volumetric flow rate is decreased from a stable range, a range of slightly unstable flow is entered. In this range, there appears to be a partial reversal of flow in the diffuser passage creating noises and lowering the compressor efficiency. Below this range, the compressor enters what is known as surge, wherein there are periodic complete flow reversals in the diffuser passage, destroying the efficiency of the machine and endangering the integrity of the machine elements. Since a wide range of volumetric flow rates is desirable in many compressor applications, numerous modifications have been suggested to improve flow stability at low volumetric flow rates. One of the most accepted and successful modifications has been the addition of guide v'anes in the inlet of the compressor to vary the flow direction and quantity of entering gas. However, since the instability at low flow rates is also related to the diffuser configuration, it would appear desirable to vary diffuser configuration in response to the load on the machine to provide a more flexible compressor.
It is therefore the chief object of this invention to provide a method of varying the capacity of a centrifugal compressor to provide a large range of stable flow rates.
It is another object of this invention to provide a centrifugal gas compressor having means therein to stabilize the gas flow therethrough at extremely low flow rates.
It is a further object of this invention to provide means for automatically interrelating inlet guide vane movement with movement of diffuser flow restriction means to optimize compressor efficiency over a wide range of flow rates.
The objects of this invention are attained by providing a centrifugal gas compressor with inlet guide vanes and diffuser restriction means. An annular control member, arranged for movement in a circular path, simultaneously effects the position of the inlet guide vanes and the diffuser restriction means to provide peak efiiciency at any flow rate.
Other objects and features of my invention will be apparent upon a consideration of the ensuing specification and drawings in which:
FIGURE 1 is an elevational view, partly in section of a portion of a centrifugal compressor including the impeller, inlet guide vanes, and diffuser passage, the compressor incorporating my invention.
FIGURE 2 is a view taken along line II-II of FIG- URE 1.
FIGURE 3 is a fragmentary elevational view, partly in section of the compressor in FIGURE 1, further illustrating the guide vane and diffuser restriction actuator means of my invention.
Referring more particularly to the drawing, there is shown a gas compressor 1 of the well-known centrifugal type wherein gas to be compressed is induced to flow in an axial direction into a vaned impeller connected to a suitable drive for imparting rotary motion thereto. As the gas is compressed during its travel through the compressor, it is directed radially from the impeller to a diffuser passage communicating with the tip of the impeller. The compressor includes a housing 2 with inlet passage 3 and diffuser passage 5. Only a portion of the housing is shown, it being understood that such a construction is conventional in equipment of the kind under consideration. An impeller 7, affixed to shaft 9 by nut 11 is provided in housing 2 between the inlet passage 3 and diffuser passage 5. Inlet guide vanes 13 journaled for rotation in housing 2 are positioned about the inlet passage to control the direction and quantity of gas flow therethrough. An annular control member 15 is mounted on balls 17 in stationary race 19 for movement in a circular path. A plurality of cam tracks 21 equally spaced circumferentially of annular control member 15 are provided for mating engagement with cam followers 23. Cam followers 23 are comprised of rollers 25 bolted on push rods 27. Push rods 27 are bolted to diffuser restriction ring 29 so that rotation of annual control member 15 will effect axial movement of diffuser restriction ring 29 within diffuser passage 5, note the position indicated in dotted lines, said movement conforming to the shape and size of the tracks 21.
Arms 31, on guide vanes 13 are connected to annular control member 15 by links 33 so that rotation of annular control member 15 will also effect rotation of guide vanes 13.
A control rod 35 is mounted for rotation about its longitudinal axis to rotate annular control member 15 by means of links 37 and 39 pivotally mounted therehetween. The control rod 35 can be rotated by any well-known means (not shown) such as electric, pneumatic or hydraulic positioners responsive to an operating condition of the compressor or its associated equipment which is indicative of the load on the compressr. Thus if the compressor were to be used in a refrigeration machine, the positioning means could be responsive to the temperature of the chilled water leaving the machine, this temperature being related to the quantity of refrigerant being lifted from the low side to the high side of the machine by the compressor. If the compressor were being used to compress air, the positioning means could be responsive to ambient temperature since this is an indication of the air density and therefore the quantity of air being compressed.
As can be seen in FIGURE 3, cam tracks 21 have a specialized configuration. The track is so designed that rotation of annular control member 15 will rotate the guide vanes from full open position to a 60% closed position without restricting diffuser passage 5. If a reduction in flow greater than that caused by the guide vanes in the 60% closed position is desired, further rotation of annular control member 15 will simultaneously move guide vanes 13 between 60% closed and closed and move diffuser restriction ring to provide a diffuser capacity between and 5% of maximum. If a greater reduction than this is desired, further rotation of annular control member 15 will hold the diffuser restriction ring 3 in the 5% diffuser capacity position and move guide vanes 13 between 85% and 100% closed. By correlating guide vane movement and diffuser restriction ring movement in the manner described above, the lift capacity of the compressor is maximized over the complete range of fiow rates attainable.
While I have described a preferred embodiment of my invention, it is to be understood that my invention is not limited thereto, but may be otherwise embodied within the scope of the following claims.
I claim:
1. A centrifugal gas compressor comprising, a housing having an inlet passage and a diffuser passage formed therein, an impeller mounted in said housing between the inlet and diffuser thereof, a plurality of guide vanes pivotally mounted in the housing to vary the quantity of gas flowing through the inlet passage, diffuser restriction means including an annular diffuser member mounted for axial movement across the diffuser passage to restrict fiow of gas therethrough, actuator means including an annular control member arranged for movement in a circular path about the inlet passage connected to said guide vanes and regulating means effective in response to and operable only after a predetermining movement of the annular control member and pivoting of said guide vanes for axially positioning said annular diffuser member in response to further movement of said annular control member.
2. A centrifugal gas compressor according to claim 1 wherein said regulating means includes a plurality of cam followers attached to said diffuser restriction means, said annular control member having a plurality of cam tracks formed therein for engagement by said cam followers to move said diffuser restriction means in response to the circular movement of said annular control member.
3. A centrifugal compressor according to claim 1 wherein said actuator means further includes guide vane linkage between said annular control member and said guide vanes, said guide vane linkage means comprising arms, affixed to said guide vanes for rotation therewith, and, linking rods, pivotally connected to said annular control member and said arms to rotate said guide vanes when said annular control member is rotated.
4. A centrifugal compressor according to claim 1 wherein said actuator means further includes a control rod mounted in said housing for rotation therein, and, control rodlinkage means, operably associated with said annular control member so that rotation of said control rod effects rotation of said annular control member.
References Cited UNITED STATES PATENTS 2,645,410 7/1953 Bauger et al 230-114 3,032,259 5/1962 Jassniker 230-114 3,251,539 5/1966 Wolfe et al. 230115 3,289,919 12/1966 Wood 230-127 FOREIGN PATENTS 845,156 7/ 1952 Germany.
0 HENRY F. RADUAZO, Primary Examiner.
DONLEY I. STOCKING, Examiner.
US577447A 1966-09-06 1966-09-06 Centrifugal gas compressor Expired - Lifetime US3362625A (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
US577447A US3362625A (en) 1966-09-06 1966-09-06 Centrifugal gas compressor
GB35032/67A GB1190796A (en) 1966-09-06 1967-07-31 Centrifugal Gas Compressor
JP42051643A JPS5010001B1 (en) 1966-09-06 1967-08-11
FR1549304D FR1549304A (en) 1966-09-06 1967-09-04
NL6712176A NL6712176A (en) 1966-09-06 1967-09-05
DE19671628232 DE1628232C (en) 1966-09-06 1967-09-06 Centrifugal compressor

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FR (1) FR1549304A (en)
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Cited By (38)

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Publication number Priority date Publication date Assignee Title
US4219305A (en) * 1978-12-26 1980-08-26 Carrier Corporation Diffuser control
US4257733A (en) * 1978-12-26 1981-03-24 Carrier Corporation Diffuser control
US4288198A (en) * 1979-03-12 1981-09-08 Hitachi, Ltd. Method of controlling multistage centrifugal compressor equipment
US4460310A (en) * 1982-06-28 1984-07-17 Carrier Corporation Diffuser throttle ring control
US4718819A (en) * 1983-02-25 1988-01-12 Teledyne Industries, Inc. Variable geometry device for turbine compressor outlet
US4780055A (en) * 1986-04-24 1988-10-25 Aktiengesellschaft Kuhnle, Kopp & Kausch Axial torque governor for a turbo-supercharger for internal combustion engines
EP0331902A2 (en) * 1988-02-26 1989-09-13 Hitachi, Ltd. Diffuser for a centrifugal compressor
US5362203A (en) * 1993-11-01 1994-11-08 Lamson Corporation Multiple stage centrifugal compressor
EP0811770A1 (en) * 1996-06-07 1997-12-10 Carrier Corporation Variable pipe diffuser for centrifugal compressor
EP0896157A1 (en) 1997-08-06 1999-02-10 Carrier Corporation Drive positioning mechanism with backlash adjustment for variable pipe diffuser
US5895204A (en) * 1997-08-06 1999-04-20 Carrier Corporation Drive positioning mechanism for a variable pipe diffuser
US5899661A (en) * 1997-08-06 1999-05-04 Carrier Corporation Axial restraint system for variable pipe diffuser
US5915920A (en) * 1997-08-06 1999-06-29 Carrier Corporation Roller positioning system or variable pipe diffuser
US5988977A (en) * 1997-08-06 1999-11-23 Carrier Corporation Backlash adjustment mechanism for variable pipe diffuser
US6015259A (en) * 1997-08-06 2000-01-18 Carrier Corporation Support mechanism of inner ring for variable pipe diffuser
US6099168A (en) * 1997-08-06 2000-08-08 Carrier Corporation Composite roller bearing for variable pipe diffuser
EP1452742A1 (en) * 2003-02-05 2004-09-01 Borg Warner Inc. Pre-whirl generator for radial compressor
US6814540B2 (en) 2002-10-22 2004-11-09 Carrier Corporation Rotating vane diffuser for a centrifugal compressor
FR2872216A1 (en) * 2004-06-24 2005-12-30 Bosch Gmbh Robert COMPRESSION DEVICE
US20070154302A1 (en) * 2005-12-30 2007-07-05 Ingersoll-Rand Company Geared inlet guide vane for a centrifugal compressor
WO2011056167A1 (en) * 2009-11-03 2011-05-12 Ingersoll-Rand Company Inlet guide vane for a compressor
US20110297111A1 (en) * 2010-06-07 2011-12-08 Schaeffler Technologies Gmbh & Co. Kg Sealing for a regulable coolant pump
WO2012038407A1 (en) * 2010-09-22 2012-03-29 Siemens Aktiengesellschaft Turbocompressor having a simultaneously adjustable inlet guide vane and a diffuser
US20120121403A1 (en) * 2009-07-20 2012-05-17 Cameron International Corporation Removable throat mounted inlet guide vane
EP2733361A4 (en) * 2011-07-13 2015-05-20 Ihi Corp Turbocompressor
US20150219110A1 (en) * 2011-12-01 2015-08-06 Carrier Corporation Centrifugal Compressor Startup Control
WO2017015443A1 (en) * 2015-07-22 2017-01-26 Carrier Corporation Diffuser restriction ring
EP3073124A4 (en) * 2013-11-18 2017-07-26 Gree Electric Appliances, Inc. of Zhuhai Centrifugal compressor and centrifugal water chilling unit
US10006356B2 (en) 2015-02-23 2018-06-26 Ford Global Technologies, Llc Exhaust gas-turbocharged internal combustion engine comprising a radial compressor with guide device arranged in the diffuser, and method for operating an internal combustion engine of said type
CN108571462A (en) * 2017-03-10 2018-09-25 盖瑞特交通公司 The centrifugal compressor of adjustable TRIM for turbocharger
US10330105B2 (en) 2013-08-27 2019-06-25 Danfoss A/S Compressor including flow control insert and electromagnetic actuator
US11421699B2 (en) 2017-09-25 2022-08-23 Johnson Controls Tyco IP Holdings LLP Compact variable geometry diffuser mechanism
US20220389937A1 (en) * 2019-10-31 2022-12-08 Daikin Industries, Ltd. Inlet guide vane actuator assembly
US11591926B2 (en) 2020-09-23 2023-02-28 Borgwarner Inc. Turbocharger including a switchable trim compressor and ported shroud
EP4177476A1 (en) * 2021-11-03 2023-05-10 Trane International Inc. Interstage capacity control valve with side stream flow distribution and flow regulation for multi-stage centrifugal compressors
EP4177477A1 (en) * 2021-11-03 2023-05-10 Trane International Inc. Compressor interstage throttle, and method of operating therof
US11661949B2 (en) 2020-04-30 2023-05-30 Trane International Inc. Interstage capacity control valve with side stream flow distribution and flow regulation for multi-stage centrifugal compressors
US11859621B2 (en) 2020-04-30 2024-01-02 Trane International Inc. Interstage capacity control valve with side stream flow distribution and flow regulation for multi-stage centrifugal compressors

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CH677956A5 (en) * 1986-07-02 1991-07-15 Carrier Corp
DE4002548C3 (en) * 1990-01-29 1995-01-26 Kuehnle Kopp Kausch Ag Axial swirl controller for large-volume radial compressors
CN107654419A (en) * 2017-10-30 2018-02-02 珠海格力电器股份有限公司 Adjustable diffuser type and centrifugal compressor
CN114483629B (en) * 2022-01-13 2023-07-28 江苏海拓宾未来工业科技集团有限公司 Multi-shaft multi-stage hydrogen fuel high-speed centrifugal compressor

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US2645410A (en) * 1947-05-05 1953-07-14 Construction De Moteurs D Avia Gaseous fluid compressor
US3032259A (en) * 1957-12-23 1962-05-01 Sulzer Ag Turbocompressor having a radial diffuser
US3251539A (en) * 1963-05-15 1966-05-17 Westinghouse Electric Corp Centrifugal gas compressors
US3289919A (en) * 1964-11-16 1966-12-06 Westinghouse Electric Corp Centrifugal gas compressors

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Publication number Priority date Publication date Assignee Title
DE845156C (en) * 1941-12-18 1952-07-28 Kuehnle Ag Adjustment gear for star-bearing axles of flow machines
US2645410A (en) * 1947-05-05 1953-07-14 Construction De Moteurs D Avia Gaseous fluid compressor
US3032259A (en) * 1957-12-23 1962-05-01 Sulzer Ag Turbocompressor having a radial diffuser
US3251539A (en) * 1963-05-15 1966-05-17 Westinghouse Electric Corp Centrifugal gas compressors
US3289919A (en) * 1964-11-16 1966-12-06 Westinghouse Electric Corp Centrifugal gas compressors

Cited By (53)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4219305A (en) * 1978-12-26 1980-08-26 Carrier Corporation Diffuser control
US4257733A (en) * 1978-12-26 1981-03-24 Carrier Corporation Diffuser control
US4288198A (en) * 1979-03-12 1981-09-08 Hitachi, Ltd. Method of controlling multistage centrifugal compressor equipment
US4460310A (en) * 1982-06-28 1984-07-17 Carrier Corporation Diffuser throttle ring control
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Also Published As

Publication number Publication date
JPS5010001B1 (en) 1975-04-17
NL6712176A (en) 1968-03-07
GB1190796A (en) 1970-05-06
FR1549304A (en) 1968-12-13
DE1628232B2 (en) 1972-10-26
DE1628232A1 (en) 1971-08-05

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