US3672786A - Capacity control mechanism for centrifugal gas compressors - Google Patents

Capacity control mechanism for centrifugal gas compressors Download PDF

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Publication number
US3672786A
US3672786A US85937A US3672786DA US3672786A US 3672786 A US3672786 A US 3672786A US 85937 A US85937 A US 85937A US 3672786D A US3672786D A US 3672786DA US 3672786 A US3672786 A US 3672786A
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US
United States
Prior art keywords
plates
passage
gas
pivot
capacity control
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.)
Expired - Lifetime
Application number
US85937A
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English (en)
Inventor
Gordon L Mount
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
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Carrier Corp
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Publication date
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Publication of US3672786A publication Critical patent/US3672786A/en
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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
    • 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
    • F04D29/44—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
    • 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
    • F05D2260/00—Function
    • F05D2260/14—Preswirling

Definitions

  • a pair of capacity control damper plates of semi-circular form are mounted for movement about a common pivot in the gas intake passage of a centrifugal compressor. The adjacent straight or diametrical edges of the plates extend normal to the axis of the pivot.
  • a powered actuator is mounted upstream from the valve plates and is connected to the same by links. The plates are moved in unison in opposite directions about the pivot by the actuator, between positions wherein the plates extend transversely across the passage and a position in which the plates are parallel with the passage.
  • a pair of damper plates are mounted in the compressor intake passage on a common pivot.
  • the plates are of semi-circular form and are arranged with their straight edges extending normal to the pivot axis.
  • Each plate is connected by a link to a prime mover which functions to simultaneously move the plates about the pivot in opposite directions from closed to open position. Due to the form and movement of the damper plates from closed position toward open position, they impart a swirl of considerable magnitude to the gas, the swirl being in the direction of rotation of the impeller, effecting a reduction in the load on the impeller driver.
  • FIG. 1 is a lengthwise sectional view of a portion of the intake manifold and contiguous portion of a centrifugal compressor, the view including an embodiment of my invention shown in side elevation;
  • FIG. 2 is a transverse sectional view taken on line 22 of FIG. 1;
  • FIG. 3 is a view taken on a line corresponding to line 33 of FIG. 1 with a portion of the intake manifold in section;
  • FIG. 4 is a view taken on line 4-4 of FIG. 1 with the damper plates moved from closed position about 45 degrees towards open position, the view illustrating the swirl imparted to gas passing through the manifold.
  • FIG. 1 designates a portion of the casing of a centrifugal gas compressor and including an inlet portion 11.
  • An impeller 12 is mounted on a power driven shaft 13 journaled in the casing.
  • An intake manifold 17 is fixed to the inlet portion 11 of the compressor,
  • the manifold is formed with a downwardly curved portion 20.
  • a pivot pin 21 is disposed diametrically across the intake passage 23 of the manifold 17.
  • a pair of damper plates 25, 27 are pivotally mounted in side-by-side relation on the pin 21. These plates are semi-circular in form, their straight or diametrical edges being indicated at 28 (FIGS. 2, 3 and 4), and extend normal to the axis of the pivot pin 21.
  • the ends of the pin may be journaled in bearing caps 22 threaded in the side wall of the intake manifold. That arrangement prevents the escape of gas from the manifold.
  • Each of the damper plates is formed with an ear or projection 31 on the side of the plate facing upstream in the passage 23.
  • An actuator shown as a motor 33 having a gear reduction, is mounted in an area or chamber 35 formed in the manifold 17 and offset from the intake passage 23 (see FIG. 1).
  • the output shaft 37 of the actuator 33 is provided with a crank arm 40' having a journal 41.
  • Links 43 are pivotally connected at like ends to each of the ears 31; and at their opposite ends, the links 43 are journaled on the crank throw 41.
  • the chamber 35 is provided with a removable closure 45, the closure being attached to the manifold by screws 47.
  • the damper plates 25, 27 are shown in closed position; that is, the plates extend diametrically across the intake passage 23, closing the same.
  • rotation of the crank 40 in conjunction with the links 43, effects pivotal movement of the damper blades 25, 27 about the pin 21 to the position indicated in the dotted outline, FIG. 1.
  • the damper plates lie parallel to the passage 23, permitting full flow of gas to the impeller 12.
  • the ears 31 on damper plates 25, 27 are located on opposite sides of the pivot pin 21 (see FIGS. 1 and 2). Accordingly, upon operation of the actuating motor 33 the bottom portion of plate 27 is moved forwardly. Simultaneously, the top portion of plate 25 is moved forwardly, that is, the damper plates 25, 27 are tilted in opposite directions.
  • the damper plates 25, 27 have been moved from the closed position shown in solid line in FIG. 1 partially toward the open position shown in the dashed line in that figure. Upon such movement, the lower portion of the plate 27 is moved toward the impeller 12; therefore, gas moving through passage 23 sweeps downwardly along the inclined plate 27. On the other hand, the damper plate 25 is tilted in the opposite direction so that the gas sweeps upwardly along the plate 25. As disclosed, the plates 25, 27 are of semi-circular form. Accordingly, as the gas sweeps upwardly along the inclined plate 25, and contacts the curved wall of the manifold 17, circular motion is imparted to the gas, such motion being indicated by the arrows '50 in FIG. 4.
  • Imparting the swirling or rotating motion to the gas in the direction of impeller rotation reduces the load on the impeller driver and accordingly elfects a reduction in power consumption. This is particularly important upon start-up of the compressor in that the impeller is not fully loaded until the damper plates have been moved about the pivot rod 21 to the full open position shown in solid line, FIG. 1.
  • a centrifugal gas compressor having a gas intake passage for the flow of gas into the compressor, a split damper capacity control mechanism for controlling the flow of gas through said passage to the compressor, said split damper mechanism comprising a pivot pin extending in a direction diametrically of said intake passage, a pair of semi-circular damper plates having diametrically extending straight edges and mounted for movement about the axis of said pivot pin, the diametrically extending straight edges of said plates being disposed in close proximity and extending in a direction normal to the axis of said pivot pin, said pivot pin extending through said damper plates normal to the straight edges thereof, the ends of said pin terminating in closed cap members mounted in the wall of said intake passage, said plates in co-planar position extending transversely of said passage serving to close the same, a power-operated driver means mounted in said passage in upstream relation to said plates, a pair of links extending from said powered driver means and being pivotally connected at their like ends to said plates respectively, said driver in conjunction with said links being operable

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Control Of Positive-Displacement Air Blowers (AREA)
  • Lift Valve (AREA)
US85937A 1970-11-02 1970-11-02 Capacity control mechanism for centrifugal gas compressors Expired - Lifetime US3672786A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US8593770A 1970-11-02 1970-11-02

Publications (1)

Publication Number Publication Date
US3672786A true US3672786A (en) 1972-06-27

Family

ID=22194965

Family Applications (1)

Application Number Title Priority Date Filing Date
US85937A Expired - Lifetime US3672786A (en) 1970-11-02 1970-11-02 Capacity control mechanism for centrifugal gas compressors

Country Status (6)

Country Link
US (1) US3672786A (enExample)
JP (1) JPS5010002B1 (enExample)
CH (1) CH525397A (enExample)
DE (1) DE2134242B2 (enExample)
FR (1) FR2113464A5 (enExample)
GB (1) GB1315433A (enExample)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3904309A (en) * 1974-08-12 1975-09-09 Caterpillar Tractor Co Variable angle turbine nozzle actuating mechanism
US3922108A (en) * 1974-03-18 1975-11-25 Wallace Murray Corp Pre-whirl turbo charger apparatus
US3937591A (en) * 1972-11-06 1976-02-10 Outokumpu Oy Controlling a sludge flow
US5605435A (en) * 1994-05-06 1997-02-25 Ingersoll-Rand Company Method and apparatus to achieve passive damping of flow disturbances in a centrifugal compressor to control compressor surge
WO2005100798A1 (en) * 2004-04-13 2005-10-27 Integral Powertrain Ltd A pre-whirl generator, a compressor and a method of imparting pre-whirl to a gas flow
US20060255303A1 (en) * 2005-05-12 2006-11-16 Honeywell International, Inc. Dual-actuator aircraft environmental control system valve
US20090139228A1 (en) * 2007-12-04 2009-06-04 Mann+Hummel Gmbh Exhaust Gas Turbocharger for An Internal Combustion Engine and Device for Switching An Air Guiding Device of An Exhaust Gas Turbocharger
WO2019170280A1 (de) * 2018-03-09 2019-09-12 Ihi Charging Systems International Gmbh Luftführungsabschnitt für einen abgasturbolader und abgasturbolader
US11208971B2 (en) * 2019-01-16 2021-12-28 Ford Global Technologies, Llc Methods and systems for mitigating condensate formation
CN114514380A (zh) * 2019-10-16 2022-05-17 株式会社Ihi 离心压缩机

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB0821089D0 (en) 2008-11-19 2008-12-24 Ford Global Tech Llc A method for improving the performance of a radial compressor

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3937591A (en) * 1972-11-06 1976-02-10 Outokumpu Oy Controlling a sludge flow
US3922108A (en) * 1974-03-18 1975-11-25 Wallace Murray Corp Pre-whirl turbo charger apparatus
US3904309A (en) * 1974-08-12 1975-09-09 Caterpillar Tractor Co Variable angle turbine nozzle actuating mechanism
US5605435A (en) * 1994-05-06 1997-02-25 Ingersoll-Rand Company Method and apparatus to achieve passive damping of flow disturbances in a centrifugal compressor to control compressor surge
US5611664A (en) * 1994-05-06 1997-03-18 Ingersoll-Rand Company Apparatus to achieve passive damping of flow disturbances in a centrifugal compressor to control compressor surge
WO2005100798A1 (en) * 2004-04-13 2005-10-27 Integral Powertrain Ltd A pre-whirl generator, a compressor and a method of imparting pre-whirl to a gas flow
US20060255303A1 (en) * 2005-05-12 2006-11-16 Honeywell International, Inc. Dual-actuator aircraft environmental control system valve
US7264017B2 (en) 2005-05-12 2007-09-04 Honeywell International, Inc. Dual-actuator aircraft environmental control system valve
US20090139228A1 (en) * 2007-12-04 2009-06-04 Mann+Hummel Gmbh Exhaust Gas Turbocharger for An Internal Combustion Engine and Device for Switching An Air Guiding Device of An Exhaust Gas Turbocharger
US8156741B2 (en) * 2007-12-04 2012-04-17 Mann + Hummel Gmbh Exhaust gas turbocharger for an internal combustion engine and device for switching an air guiding device of an exhaust gas turbocharger
WO2019170280A1 (de) * 2018-03-09 2019-09-12 Ihi Charging Systems International Gmbh Luftführungsabschnitt für einen abgasturbolader und abgasturbolader
US11255256B2 (en) 2018-03-09 2022-02-22 Ihi Charging Systems International Gmbh Air-guiding section for an exhaust turbocharger and exhaust turbocharger
US11208971B2 (en) * 2019-01-16 2021-12-28 Ford Global Technologies, Llc Methods and systems for mitigating condensate formation
CN114514380A (zh) * 2019-10-16 2022-05-17 株式会社Ihi 离心压缩机
CN114514380B (zh) * 2019-10-16 2024-03-01 株式会社Ihi 离心压缩机

Also Published As

Publication number Publication date
DE2134242B2 (de) 1975-10-09
FR2113464A5 (enExample) 1972-06-23
DE2134242A1 (de) 1972-05-18
JPS5010002B1 (enExample) 1975-04-17
CH525397A (de) 1972-07-15
GB1315433A (en) 1973-05-02

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