US2322338A - Axial flow compressor plant - Google Patents

Axial flow compressor plant Download PDF

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Publication number
US2322338A
US2322338A US253838A US25383839A US2322338A US 2322338 A US2322338 A US 2322338A US 253838 A US253838 A US 253838A US 25383839 A US25383839 A US 25383839A US 2322338 A US2322338 A US 2322338A
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United States
Prior art keywords
compressor
volume
pressure
axial flow
point
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Expired - Lifetime
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US253838A
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English (en)
Inventor
Baumann Adolf
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BBC Brown Boveri AG Germany
BBC Brown Boveri France SA
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BBC Brown Boveri France SA
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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
    • 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

Definitions

  • This invention relates to axial flow compressors and to mechanisms for regulating the compressor output. and preventing surging.
  • the characteristic curves for an axial flow compressor are basically difierent from the corresponding curves for radial flow compressors and the methods of regulation that are applicable for radial flow compressors are not satisfactory in the case of axial flow compressors.
  • Objects of this invention are to provide axial flow compressors with new mechanisms for regulating the same, the apparatus and methods being characterized by high efficiency and stability of operation at low compressor outputs.
  • An object is to provide compressor plants including an axial flow compressor, an engine or motor for driving the compressor at a substantially con-- stant speed for which the compressor. output will satisfy the maximum volume and/or pressure demands, an air or gas turbine, and a manually or automatically controlled valve for diverting to the turbine such fraction of the total amount of air or gas pumped by the compressor as will result in the desired regulation condition at the point of use of the compressed air or gas, i. e. constant pressure, constant volume,'predetermined pressure-volume characteristic, etc.; the power developed by the turbine being employed to supplement the engine or motor.
  • An object is to provide axial flow compressors that have mechanisms operable to maintain a desired condition of constant pressure, constant volume or predetermined pressure-volume relationship at the point of use of the compressed'air Or gas when a constant speed motor drives the compressor at a speed such that the maximum volume demand is delivered at the required pressure, the regulating mechanism being operable to divert through an expansion turbine such fraction of the compressor output which will maintain the desired condition.
  • Fig. 1 is a curve sheet showing the pressurevolume and load-volume characteristics for axial flow and radial flow compressors
  • Figs. 2 to 5, inclusive are similar characteristic curves for axial flow compressors regulated in accordance with this invention.
  • FIG. 6 is a diagrammatic illustration of an axial flow compressor plant embodying this invention.
  • the heavy solid line curves La, Pa show the variation of the load L and' discharge pressure P of an axial flow compressor with changes in the output or volume V of gas or air delivered by the compressor
  • the heavy dotted line curves, Lr, Pr show the corresponding variations'in the case of a radial flow compressor.
  • the designs of the two compressors are assumed to be such that the power inputs to the compressors are equal when they deliver the same normal volume Vn of air or gas at the same pressure. This condition is indicated by the crossing of the pressure curves Pa, Pr and the load -curves La, Lr at points I, I", respectively.
  • the normal volume Vn is pumped through the compressor at the pressure level P3-l, and the fraction in excess of the required volume V3 is blown off, 'thus holding the power input at the valueL'a when the compressed gas or air is discharged at atmospheric pressure.
  • This blow off at the normal discharge pressure insures stable operation but the power input L'a is substantially above the corresponding power input Irr for the radial flow compressor at reduced outputs.
  • Increased efllciency is obtained by discharging the surplus gas or air through an expansion turbine coupled to the compressor, the net power input to the axial flow compressorunit then droppin along curve L"a as the volume demand decreases.
  • Line L"a drops below curve Lr and thus indicates that axial flow compressor and expansion turbine system is more eincient than the radial flow compressor at low outputs.
  • the discharge pressure is kept constant over a range or output demand and it is not necessary to provide additional regulating members or to alter the rotary speed of the compressor to prevent surging.
  • ment may be expanded in a turbine to supply power for driving the compressor, and the net power input is thereby reduced still further to.
  • the expansion turbine serves as a regulating member for establishing the desired condition and for preventing surging.
  • the regulated condition may be that of a constant volume, for example V3, that may normally be supplied at a pressure P2 corresponding to operating point 2 on the curve Pa.
  • the output of the compressor at operating point 2 exceeds the demand require! ment V3 by a surplus AV that may be discharged through the recovery turbine.
  • the power consumption' when operating at point 2 on curve Pa is substantially less than that for. operation at point I at which the required volume V3 constitutes the total compressor output at a pressure PI.
  • the power consumption at operating point deliverypressure is the maximum volume that can be discharged at that pressure and the sur plus AV or A'V above the actual demand at pressure PI or P3, respectively, is blown off to the expansion turbine through a pressure-regulating valve. and the net power input drops with decreasing consumption along the net load lines L and L respectively, as -the consumed volume varies between points I and 2 on pressure line PI and points 3 and l on pressure line P3.
  • Another type oi! regulated condition is that oi! simultaneous variation of pressure with changmg volume demand in accordance with a selected parabolic pressure-volume curve such as indicated by lines A or B of Fig. 5.
  • the particular parabolic curve of operatingconditions is set by hand adjustment and the axial flow compressor is driven at that speed for which the pressurevolume curve Pa crosses the control condition line A at operating point I corresponding to maximum compressor output at the maximum demand pressure.
  • a greater or less surplus volume AV is blown oil? to obtain the corresponding reduction in outlet pressure, and the operating point drops to point 2 on curve Pa when the delivery pressure falls to point 3 on curve A.
  • the correspond ing drop inthe load is from point I to point 2' on the load curve La when the surplus volume AV is discharged to open air, or from point I to point 3 on curve L if the expansion turbine is used.
  • a greater surplus volume A'V may be available when the control member is set for operation on curve B corresponding to a smaller volume consumption.
  • the speed regulating methods without requiring I is indicated by point I' of curve La, and the power drops to point 2' on curve La if the surplus volume AV is exhausted to atmosphere or to point 3' of curve La-- if the surplus is discharged through the turbine.
  • Any desired volume for example volume V4, may be set in the usual way by adjusting the regulating member by hand.
  • the surplus A'V may be employed in the turbine to reduce the power input to point 4', and surging is prevented at all reduced demand volumes as the same volume V2 is discharged by the compressor regardless of the lesser volume that is to be supplied to the point of use.
  • the regulated condition may be that of constant pressure PI or P3 corresponding to operating points auxiliary surging gears to insure stable operation; the compressor at all times delivering the full volume along the pressure-volume characteristic and any surplus being delivered to the expansion turbine to reduce the power consumption.
  • the lating equipment includes the axial flow compressor C and expansion turbine T on the same shaft S with a motor or engine M.
  • the compressor has a suction line II and pressure line I2 forsupplying compressed air or gas to a conduit I3 that leads to the point of use and to the intake line ll of the turbine T.
  • the intake line I4 has a regulating member or valve I5 for controlling that fraction of the total compressor output that is to be delivered to the turbine to maintain the desired control condition in delivery conduit I3.
  • the turbine exhaust line I6- may include a valve I! to control the discharge of the exhaust to open air or, alternatively, to return the exhaust gas or air through line I8 to the suction line I I of the compressor.
  • control valves and mechanisms for regulating the venting of the surplus compressor output to atmosphere or to the turbine may' be of various known manual and sure is not less than the maximum volume demand, a, delivery conduit into which said pressure line opens, and regulating means to prevent surging and to maintain a desired operating condition at said delivery line when the load demand drops below its maximum value; said regulating means comprising a. conduit branching from said pressure line, and a regulating valve in said branch conduit for diverting from the delivery conduit that portion of the compressor output which at the constant operating speed exceeds the volume corresponding to the desired operating condition at the delivery line, said regulating means including also power recovery means for decreasing the load imposed on said power means

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  • Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Positive-Displacement Air Blowers (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US253838A 1938-02-01 1939-01-31 Axial flow compressor plant Expired - Lifetime US2322338A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE524593X 1938-02-01

Publications (1)

Publication Number Publication Date
US2322338A true US2322338A (en) 1943-06-22

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US253838A Expired - Lifetime US2322338A (en) 1938-02-01 1939-01-31 Axial flow compressor plant

Country Status (4)

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US (1) US2322338A (de)
CH (1) CH213987A (de)
FR (1) FR849345A (de)
GB (1) GB524593A (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3495766A (en) * 1968-01-11 1970-02-17 Gen Motors Corp Method and means for increasing the maximum pressure ratio of a turbine driven centrifugal compressor
US3826594A (en) * 1971-07-02 1974-07-30 Ingersoll Rand Co Gas compressor
US20100272588A1 (en) * 2009-04-28 2010-10-28 Alberto Scotti Del Greco Energy recovery system in a gas compression plant

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3495766A (en) * 1968-01-11 1970-02-17 Gen Motors Corp Method and means for increasing the maximum pressure ratio of a turbine driven centrifugal compressor
US3826594A (en) * 1971-07-02 1974-07-30 Ingersoll Rand Co Gas compressor
US20100272588A1 (en) * 2009-04-28 2010-10-28 Alberto Scotti Del Greco Energy recovery system in a gas compression plant
ITMI20090724A1 (it) * 2009-04-28 2010-10-29 Nuovo Pignone Spa Sistema di recupero dell'energia in un impianto per la compressione di gas
CN101876323A (zh) * 2009-04-28 2010-11-03 诺沃皮尼奥内有限公司 气体压缩设备中的能量回收系统
US8567184B2 (en) * 2009-04-28 2013-10-29 Nuovo Pignone S.P.A. Energy recovery system in a gas compression plant
CN101876323B (zh) * 2009-04-28 2014-12-10 诺沃皮尼奥内有限公司 气体压缩设备中的能量回收系统

Also Published As

Publication number Publication date
GB524593A (en) 1940-08-09
CH213987A (de) 1941-03-31
FR849345A (fr) 1939-11-21

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