US3240422A - Method of and apparatus for the prevention of surging with axial compressors - Google Patents

Method of and apparatus for the prevention of surging with axial compressors Download PDF

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Publication number
US3240422A
US3240422A US268306A US26830663A US3240422A US 3240422 A US3240422 A US 3240422A US 268306 A US268306 A US 268306A US 26830663 A US26830663 A US 26830663A US 3240422 A US3240422 A US 3240422A
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Prior art keywords
compressor
regulator
surge
blading
surging
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Expired - Lifetime
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US268306A
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English (en)
Inventor
Pettersen Johan
Baumann Hans
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BBC Brown Boveri AG Germany
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Bbc Brown Boveri & Cie
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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

  • the present invention relates to an improved method for the prevention of surging with single or multi-stage axial compressors and to an apparatus for putting this method into practice.
  • the surge limit a (FIG. 1) is fixed by experiment.
  • a line b is now chosen at an appropriate distance from this limit, this acting as the limit of approach for the surge-prevention regulator.
  • surge limit a can displace itself in the direction of the limit of approach b of the regulator, e.g. due to contamination of the blading or change in the gas inlet temeprature, so that the safety factor becomes too small.
  • the limit of approach is de- "ice termined on the basis of measurements at commissioning and thereafter remains constant, it can happen that the compressor begins to surge despite perfect functioning of the regulation.
  • FIGS. 2 and 3 are represented schematically two constructional examples of the invention, whereby like components are denoted by the same reference symbols. Detail views of them are given in FIGS. 4 and 5.
  • the axial compressor 1 isdriven by motor 2, draws gas in from connection line 3 and passes it thru outlet connection line 4.
  • Vibration feelers 6 are mounted on the guide blades 5, the impulses from the former being transmitted as an input parameter to regulator 7 via an amplifier 8.
  • a maximal permissable value which is declared by the proximity of the surge limit--the regulator is acutated. It opens an outflow 9 through which control oil runs out of the pressure system 10, the feed 11 to which is adjusted by orifice 12.
  • control piston 13 of the servo-motor 14 opens the blow-off valve 15 from output line 4 and thus makes an additional outlet available to the compressed gases.
  • the output volume becomes greater once more, the operating point of the compressor falls back into the region of stable flow because of thisto the right in FIG. 1-and the Surging is prevented. If the blade vibrations fade away again, regulator 7 closes off the outflow 9, the pressure in system 10 increases and piston 13 of servo-motor 14 shuts the blow-oil valve 15.
  • FIG. 3 shows another possible application of the apparatus as according to the invention.
  • Axial compressor 1, motor 2, line connections 3 and 4, outflow 9, pressureoil system 10, oil feed 11, orifice 12, control piston 13 of the servo-motor 14 and the blow-off valve 15 have the same function as in FIG. 2.
  • the outflow 9 together with the blow-off valve 15 are now, however, actuated by a surge-prevention regulator 16 which is already given in the introduction to the description as being known. It is commented on only briefly here.
  • the surge prevention regulator is provided with a pressure difference measuring apparatus 17 on the membrane 18 of which acts the pressure difierence at the throughput measuring point 19 in the suction connection 3. Should the throughput quantity or, respectively the pressure difference at the measuring point 19 decrease to a certain minimum value, then the force exerted upwards by the membrane 18 falls below the pretension of spring 20 which now moves the oil blow-off valve 21 to the open position. As soon as oil runs out through the outflow 9, the pressure falls in the hydraulic system 10 which then causes the opening to blow-01f valve 15.
  • the characteristic value of the regulator 16, ie the minimum pressure. difference at measuring point 19 at which the membrane 18 opens the oil blow-0E valve 21, is thus determined by the pretension in the spring 20.
  • This pretension can be altered by displacing cam 22 which is set during the commissioning and which can be corrected by hand with the aid of adjustment spindle 23 in later service.
  • the form of the latter is chosen so that on displacement to the left, the pretension of spring 20 is raised.
  • the surge-prevention regulator 16 and that part of the installation as given in FIG. 3 and as described earlier are known and are frequently employed in this arrangement. It will now be shown that the apparatus as according to the invention may also be applied with advantage for this purpose.
  • vibration feelers 6 are also attached to the guide blades 5, these feelers serving to transmit the blade vibrations as impulses to the regulator 7 via amplifier 8.
  • the regulator does not act directly on the blow-off valve 15 any more.
  • regulator 7 acts on the adjustment motor 26 which actuates the adjustment spindle 23.
  • Cam 22 thus travels to the left and opens the oil blow-off valve 2 1, this then causing an opening of blow-off valve 15, as is described above.
  • the pressure in the output line 4 and at the throughout measuring point 18 remain at the same time, or leastwise at first, unchanged.
  • the function between output pressure and suction quantity was thus altered. This means that the regulator 7 has displaced the limit of approach b (FIG. 1) of the surgeprevention regulator 16 and thereby adapted it to the new, actual surge limit.
  • vibration feelers are mounted on each row of guide blades but in fact the moving blades could equally as well be called upon for this. Admittedly, there arise certain difiiculties in leading out the connecting cables from the rotor with this arrangement. In principle it is suflicient merely to mount a vibration feeler on only one guide or moving blade. Naturally, one would choose for that purpose the row of blades at which surging first occurs as given by calculation or experience. But as this can be various rows of blades depending on the changing operating conditions, it is usual to attach a vibration feeler to one blade of each endangered row. Nonetheless, the amplifier accepts only the greatest amplitude of vibration at any one time and passes this on to the regulator which comes into action as a limit regulator only from a predetermined minimum value onwards.
  • FIG. 4 is shown the application of a strain gauge 27 of which one is attached to moving blade 28 and another to guide blade 5.
  • the strain gauges are fixed to the feet of the blades as the greatest material stresses occur there due to the blade vibrations and are thus the easiest to measure.
  • the connecting'cables 29 lead to amplifier 8 which is not drawn in here.
  • FIG. shows the application of vibration guages 30.
  • vibration guages 30 For this there may be considered such appliances which measure the amplitude, the velocity or the acceleration of the blade vibrations.
  • These types of apparatus are best built into the blade tips as the blade amplitude is greatest theme and the measurement most effective.
  • the vibration gauges may also be mounted on the blade foot; in this case, however, more sensitive apparatus and a higher amplification of the impulses are then required.
  • the vibration feelers can be mounted on either one or on several rows, and both on the guide and moving blades, as is represented in FIGS. 4 and 5, or only on one of the two. If it is to be avoided that the connection cables be led out of the rotor, whereas, on the other hand it is a row of moving blades which stands in the greatest danger, then a possible advantageous method of measurement is presented if the natural frequency of the moving blade to be measured coincides with the natural frequency of the neighboring guide blade. In this case the vibrations of the moving blade are transferred synchronously on to the guide blade and can be measured there more simply.
  • the regulator 7 can act in various ways on the compressor. Arrangements are thus known with which the regulator actuates a component other than the blow-off valve or the cam of the surge-prevention regulator. It may clearly be understood that corresponding arrangements can also be effected with a regulation as according to the present invention.
  • the apparatus can also serve only for surveillance so that, should the amplitude of the blade vibrations exceed an allowable value, the impulse from the vibration feeler releases an acoustic or visual signal whereupon the necessary control measures may result from hand.
  • the apparatus can, of course, be employed to check blade vibrations of turbines, e.g. at start up whereby the regulator operates naturally on another control organ, preferably the inlet valve.
  • the method of preventing said compressor from surging which comprises the step of measuring vibrations induced in the blading as a result of fluid flow therethrough and utilizing only such measured vibrations as reach a predetermined amplitude for regulating fluid flow through the compressor in such sense as to reduce its tendency to surge.
  • Apparatus for preventing surging in an axial flow compressor having at least one stage comprising a row of stationary blading and an adjacent row of blading mounted on the compressor rotor comprising, a feeler element in direct association with said blading, said feeler element producing a signal proportional to the amplitude at which said blading vibrates, and means responsive only when said signal reaches a predetermined level for regulating fluid flow through said compressor in such sense as to reduce its tendency to surge.
  • Apparatus for preventing surging in an axial flow compressor having at least one stage comprising a row of stationary blading and an adjacent row of blading mounted on the compressor rotor, means responsive to a predetermined decrease in pressure obtained across a measuring point of said compressor for regulating fluid flow through said compressor in such sense as to reduce its tendency to surge, means for adjusting the pressure at which said regulating means becomes operative, a feeler element in direct association with said blading, said feeler element producing a signal proportional to the References Cited by the Examiner UNITED STATES PATENTS 2,395,995 3/1946 Dewey 23017 2,424,137 7/1947 Ball 230115 2,455,292 11/1948 Borden 230-1 15 2,696,345 12/1954 Hopper 2301 14 3,058,339 10/1962 Shapiro 737 1.4

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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)
US268306A 1962-04-03 1963-03-27 Method of and apparatus for the prevention of surging with axial compressors Expired - Lifetime US3240422A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CH404862A CH394471A (de) 1962-04-03 1962-04-03 Verfahren und Einrichtung zur Pumpenverhütung bei Axialverdichtern

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US3240422A true US3240422A (en) 1966-03-15

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CH (1) CH394471A (de)
GB (1) GB994592A (de)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3677000A (en) * 1970-04-27 1972-07-18 Faulkner C Thomson System for the detection and control of compressor stall
US3930742A (en) * 1973-10-23 1976-01-06 Howell Instruments, Inc. Velocity probe for compressor surge control
US3963367A (en) * 1974-08-21 1976-06-15 International Harvester Company Turbine surge detection system
US4039267A (en) * 1974-12-18 1977-08-02 Bbc Brown Boveri & Company Limited Method and apparatus for starting a blower
US4156578A (en) * 1977-08-02 1979-05-29 Agar Instrumentation Incorporated Control of centrifugal compressors
US4230437A (en) * 1979-06-15 1980-10-28 Phillips Petroleum Company Compressor surge control system
EP0175445A1 (de) * 1984-08-20 1986-03-26 International Control Automation Finance S.A. Regulierung des Pumpens für Verdichter
US4781524A (en) * 1987-02-12 1988-11-01 Man Gutehoffnungshuette Gmbh Method and apparatus for detecting pressure surges in a turbo-compressor
US6328526B1 (en) * 1999-04-02 2001-12-11 Mitsubishi Heavy Industries, Ltd. Gas turbine starting method
CN102042092A (zh) * 2010-12-06 2011-05-04 哈尔滨工业大学 一种涡轮增压系统压气机风量切换控制的喘振保护方法
US20120103426A1 (en) * 2010-10-27 2012-05-03 Daniele Galeotti Method and device performing model based anti-surge dead time compensation
US20140219820A1 (en) * 2011-10-03 2014-08-07 Ihi Corporation Centrifugal compressor apparatus and method for preventing surge therein
EP3012460A1 (de) * 2014-10-14 2016-04-27 Simmonds Precision Products, Inc. Systeme und verfahren zur überwachung von überspannungsbedingungen

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4380893A (en) * 1981-02-19 1983-04-26 The Garrett Corporation Compressor bleed air control apparatus and method

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2395995A (en) * 1945-03-19 1946-03-05 Fluor Corp Vibration-responsive control for cooling tower fans
US2424137A (en) * 1944-04-13 1947-07-15 Chrysler Corp Control apparatus
US2455292A (en) * 1944-04-13 1948-11-30 Chrysler Corp Control apparatus
US2696345A (en) * 1949-10-14 1954-12-07 United Aircraft Corp Method of controlling supercharger to avoid pulsation
US3058339A (en) * 1958-09-02 1962-10-16 Curtiss Wright Corp Vibration detector and measuring instrument

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2424137A (en) * 1944-04-13 1947-07-15 Chrysler Corp Control apparatus
US2455292A (en) * 1944-04-13 1948-11-30 Chrysler Corp Control apparatus
US2395995A (en) * 1945-03-19 1946-03-05 Fluor Corp Vibration-responsive control for cooling tower fans
US2696345A (en) * 1949-10-14 1954-12-07 United Aircraft Corp Method of controlling supercharger to avoid pulsation
US3058339A (en) * 1958-09-02 1962-10-16 Curtiss Wright Corp Vibration detector and measuring instrument

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3677000A (en) * 1970-04-27 1972-07-18 Faulkner C Thomson System for the detection and control of compressor stall
US3930742A (en) * 1973-10-23 1976-01-06 Howell Instruments, Inc. Velocity probe for compressor surge control
US3963367A (en) * 1974-08-21 1976-06-15 International Harvester Company Turbine surge detection system
US4039267A (en) * 1974-12-18 1977-08-02 Bbc Brown Boveri & Company Limited Method and apparatus for starting a blower
US4156578A (en) * 1977-08-02 1979-05-29 Agar Instrumentation Incorporated Control of centrifugal compressors
US4230437A (en) * 1979-06-15 1980-10-28 Phillips Petroleum Company Compressor surge control system
EP0175445A1 (de) * 1984-08-20 1986-03-26 International Control Automation Finance S.A. Regulierung des Pumpens für Verdichter
US4781524A (en) * 1987-02-12 1988-11-01 Man Gutehoffnungshuette Gmbh Method and apparatus for detecting pressure surges in a turbo-compressor
US6328526B1 (en) * 1999-04-02 2001-12-11 Mitsubishi Heavy Industries, Ltd. Gas turbine starting method
US20120103426A1 (en) * 2010-10-27 2012-05-03 Daniele Galeotti Method and device performing model based anti-surge dead time compensation
US9127684B2 (en) * 2010-10-27 2015-09-08 Nuovo Pignone S.P.A. Method and device performing model based anti-surge dead time compensation
CN102042092A (zh) * 2010-12-06 2011-05-04 哈尔滨工业大学 一种涡轮增压系统压气机风量切换控制的喘振保护方法
CN102042092B (zh) * 2010-12-06 2013-05-29 哈尔滨工业大学 一种涡轮增压系统压气机风量切换控制的喘振保护方法
US20140219820A1 (en) * 2011-10-03 2014-08-07 Ihi Corporation Centrifugal compressor apparatus and method for preventing surge therein
US10202980B2 (en) * 2011-10-03 2019-02-12 Ihi Rotating Machinery Engineering Co., Ltd. Centrifugal compressor apparatus and method for preventing surge therein
EP3012460A1 (de) * 2014-10-14 2016-04-27 Simmonds Precision Products, Inc. Systeme und verfahren zur überwachung von überspannungsbedingungen
US10317276B2 (en) 2014-10-14 2019-06-11 Simmonds Precision Products, Inc. Systems and methods for monitoring surge conditions

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Publication number Publication date
GB994592A (en) 1965-06-10
CH394471A (de) 1965-06-30

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