EP2126367B1 - Mehrstufiger turbogassystemverdichter - Google Patents

Mehrstufiger turbogassystemverdichter Download PDF

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Publication number
EP2126367B1
EP2126367B1 EP07706234.7A EP07706234A EP2126367B1 EP 2126367 B1 EP2126367 B1 EP 2126367B1 EP 07706234 A EP07706234 A EP 07706234A EP 2126367 B1 EP2126367 B1 EP 2126367B1
Authority
EP
European Patent Office
Prior art keywords
compressor
final stage
diffuser
blades
fixed
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.)
Revoked
Application number
EP07706234.7A
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English (en)
French (fr)
Other versions
EP2126367A1 (de
Inventor
Stefano Cecchi
Massimiliano Maritano
Andrea Silingardi
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.)
Ansaldo Energia SpA
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Ansaldo Energia SpA
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Application filed by Ansaldo Energia SpA filed Critical Ansaldo Energia SpA
Priority to PL07706234T priority Critical patent/PL2126367T3/pl
Publication of EP2126367A1 publication Critical patent/EP2126367A1/de
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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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/54—Fluid-guiding means, e.g. diffusers
    • F04D29/541—Specially adapted for elastic fluid pumps
    • F04D29/542—Bladed diffusers
    • F04D29/544—Blade shapes

Definitions

  • the present invention relates to a turbogas system compressor.
  • gas-turbine electric power systems normally comprise a drive (turbo) assembly comprising a compressor, a combustion chamber, a gas turbine, and a generator connected mechanically to the same shaft as the turbine and compressor, and connected to an electric distribution network by a main switch.
  • the compressor provides for drawing in a given amount of air, adequately increasing its pressure, and feeding it to the turbogas system combustion chamber.
  • the combustion chamber burns a certain amount of fuel mixed with the air compressed by the compressor, and feeds the burnt fluid to the turbine, which expands the burnt fluid to convert the potential thermal energy of the fluid to work. Part (roughly half) of the work produced by the turbine is used to drive the compressor, and the rest to drive the generator.
  • Multistage axial-flow compressors comprising an outlet diffuser duct, or so-called diffuser, at the exhaust, the purpose of which is to effectively recover part of the kinetic energy of the airflow from the final stage of the compressor, and convert it to potential pressure energy prior to supplying the combustion chamber.
  • the diffuser of compressors of this sort is normally characterized by an increase in diameter between the inlet section, close to the final stage of the compressor, and the outlet section, close to the combustion chamber, and by a curved shape giving rise to mixed flow.
  • the diffuser comprises an array of straightening blades for deflecting airflow so that air flows out of the diffuser with a slight tangential velocity component to minimize kinetic energy and maximize potential pressure energy.
  • the blades produce a pressure loss proportional to deflection of the airflow.
  • Compressors of this type are disclosed in documents WO 02/36965 , US-A-5249921 , EP-A1-0441097 , EP-A2-1111191 .
  • the increase in section along the diffuser mainly produces a reduction in velocity of the airflow evolving inside the diffuser. More specifically, as the fluid velocity is reduced by the increase in the flow area, and the tangential component is reduced by the increase in the radius of the channel defined by the diffuser (free-vortex law). The effect of the reduction in the meridian component of velocity is generally predominant, thus resulting in a significant increase in the flow angle (the angle between the airflow direction and the compressor axis) along the channel.
  • the airflow normally strikes the fixed blades of the final stage at a roughly 40-60° angle, and, as it flows through the fixed blades, undergoes a limited amount of deflection of at most 15° (the flow angle between the inlet and outlet gets smaller), so that air flows into the straightening blade array at a particularly large, roughly 60-70°, angle.
  • significant flow-deflecting action is required of the straightening blades, which results in phenomena, such as airflow separation or swirl, which greatly increase pressure losses.
  • turbogas system multistage compressor provided a turbogas system multistage compressor according to claim 1.
  • Number 1 in Figure 1 indicates a multistage, axial-flow compressor of a substantially known gas-turbine electric power system comprising compressor 1, inside which air flows; a silo-type combustion chamber; a gas turbine; and a generator connected mechanically to the same shaft as the turbine and compressor, and connected to an electric distribution network.
  • compressor 1 extends along a longitudinal axis A, and comprises a rotor 2 rotating about axis A; a blade housing 3; an inlet 4; and an outlet diffuser 5.
  • Blade housing 3 comprises a substantially conical wall 8, and is fixed to inlet 4 and diffuser 5.
  • a first stage 10, a number of intermediate stages 11, and a final stage 12 are located between inlet 4 and outlet diffuser 5, and each comprise an array of movable blades 14 and an array of fixed blades 15.
  • Movable blades 14 are equally spaced about axis A to form a ring about a corresponding ring 17 connected directly to rotor 2; while fixed blades 15, also known as stator blades, are equally spaced about axis A, and extend between an outer ring 18 and an inner ring 19.
  • inner ring 18 of fixed blades 15a may be housed indifferently inside a seat formed in wall 8 of blade housing 3, or inside a seat formed in an outer shell 26 of diffuser 5, as in the example shown in the drawing.
  • Blades 15a of final stage 12 of compressor 1 are designed to produce a deflection in airflow substantially ranging between approximately 15° and 30°, and more specifically between approximately 20° and 25°.
  • the term "deflection” is intended to mean the absolute value of the difference between the outflow angle from the array of fixed blades 15a with respect to axis A, and the inflow angle into the array of fixed blades 15a with respect to axis A. Airflow into the array of fixed blades 15a - normally characterized by an inflow angle of 40° to 50° with respect to axis A - is therefore deflected by fixed blades 15a to produce an outflow angle with respect to axis A of around 20°.
  • line L1 indicates radial distribution of the flow angle with respect to axis A at a first section I upstream from the array of fixed blades 15a of final stage 12; and line L2 indicates radial distribution of the flow angle with respect to axis A at a second section 11 downstream from the array of fixed blades 15a of final stage 12.
  • the difference between the flow angle at line L1 and the flow angle at line L2 indicates the deflection imposed by fixed blades 15a, which, in the Figure 3 example, is about 20°.
  • each fixed blade 15a of final stage 12 comprises a so-called leading edge 21 struck by the airflow; a so-called trailing edge 22, struck by the airflow; a so-called trailing edge 22, opposite leading edge 21, where the airflow leaves blade 15a; a so-called suction side or outer side 23; and a so-called pressure side or inner side 24.
  • Each fixed blade 15a has a large camber angle ranging between approximately 45° and 60°, and more specifically between approximately 48° and 54°.
  • the camber angle represents the difference between the leading edge angle and trailing edge angle of fixed blade 15a, where the leading edge angle is intended to mean the angle between a mid-line M or so-called camber line of the profile of fixed blade 15a and axis A of compressor 1 at leading edge 21, and the trailing edge angle is intended to mean the angle between mid-line M of the profile of fixed blade 15a and axis A of compressor 1 at trailing edge 22.
  • Each blade 15a of final stage 12 also has a limited deviation angle, preferably of less than 10°, where "deviation angle” is intended to mean the difference between the trailing edge angle of fixed blade 15a and the outflow angle with respect to axis A at trailing edge 22.
  • Each fixed blade 15a of final stage 12 also has a so-called front-loaded profile, which means local loading - that is, the absolute value of the local difference between the air pressure on pressure side 24 and the air pressure on suction side 23 - is maximum in a region of blade 15a substantially close to leading edge 21.
  • Figure 5 shows a graph of pressure distribution on the profile of a fixed blade 15a, where the x axis shows the profile coordinate nondimensional with respect to the axial chord (projection along axis A of the segment joining leading edge 21 and trailing edge 22).
  • the 0 value on the x axis therefore corresponds to leading edge 21 of fixed blade 15a
  • the 1 value on the x axis corresponds to trailing edge 22 of fixed blade 15a.
  • Line A shows the pressure pattern along suction side 23
  • line B shows the pressure pattern along pressure side 24, and the local difference between the two curves represents local loading, which is maximum at leading edge 21.
  • diffuser 5 comprises two shells 26 and 27, which define a curved diverging annular channel 28 of increasing cross section. More specifically, diffuser 5 comprises an inlet section 29 connected to blade housing 3 and close to final stage 12; and an outlet section 30 having a larger inner annular area than inlet section 29, and connected to a cavity 31 in turn connected to one or more preferably silo-type combustion chambers (not shown for the sake of simplicity).
  • Diffuser 5 also comprises, substantially at outlet section 30, an array of straightening blades 33, each of which is connected to shells 26 and 27, and provides for deflecting airflow so that air flows out of diffuser 5 with a small amount of kinetic energy and a large amount of potential pressure energy.
  • the increase in section along diffuser 5 mainly produces a reduction in velocity of the evolving airflow inside channel 28.
  • the flow velocity inside channel 28 can be divided into a meridian component, by which is meant the vector sum of the radial component and axial component; and a tangential component, by which is meant the velocity component projected onto a plane perpendicular to the meridian plane (containing the meridian component).
  • a meridian component by which is meant the vector sum of the radial component and axial component
  • a tangential component by which is meant the velocity component projected onto a plane perpendicular to the meridian plane (containing the meridian component).
  • line L3 shows radial distribution of the flow angle with respect to axis A at a third section III immediately upstream from the inlet to the array of straightening blades 33.
  • the difference between the flow angle at line L3 and the flow angle at line L2 indicates the variation in flow angle imposed by diffuser 5, and which, in the Figure 3 example, is roughly 25°.
  • the angle, with respect to axis A, at which air flows into the array of straightening blades 33 is at most 45-50°, to avoid significant deflection action by straightening blades 33. Conversion of the kinetic energy of the airflow into potential pressure energy is therefore improved, by the improved inflow angle into straightening blades 33 eliminating the risk of pressure losses caused by the formation of swirl and separation of the airflow.
  • the present invention has the following advantages.
  • a compressor 1 in which fixed blades 15a of final stage 12 are designed to impose significant deflection of the evolving airflow inside compressor 1, improves the efficiency with which kinetic energy is converted to potential pressure energy.
  • the deflection imposed by the fixed blades of the final stage improves the angle at which air flows into the array of straightening blades 33, thus minimizing pressure losses caused by the formation of swirl and separation of the airflow.
  • compressor 1 requires only minor, low-cost structural alterations, which provide for a considerable improvement in performance in terms of efficiency of the turbogas system.
  • fixed blades 15a of final stage 12 guarantee stability of compressor 1, in particular by preventing it from reaching the limit, so-called pumping, condition.
  • the profile of fixed blades 15a combines superior aerodynamic performance with construction features enabling them to be installed in currently marketed compressors with no additional machining required. This enables application of the invention not only to new machines as original components, but also to existing machines, with no need to alter the geometry of the compressor, by simply changing the final-stage blades and possibly the inner and outer rings 19 and 18.

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

Claims (7)

  1. Turbogassystem-Mehrstufenkompressor (1), der sich entlang einer Längsachse (A) erstreckt und einen Einlass (4) und einen Auslassdiffusor (5) umfasst, zwischen denen sich nacheinander eine erste Stufe (10), eine Anzahl von Zwischenstufen (11) und eine Endstufe (12) befinden; wobei die letzte Stufe (12) eine Anordnung von fixierten Schaufeln (15a), die im Wesentlichen äquidistant um die Achse (A) des Kompressors (1) angeordnet sind und auf die der Luftstrom trifft, umfasst; wobei die fixierten Schaufeln (15a) der Endstufe (12) des Kompressors so gestaltet sind, dass sie eine Ablenkung des Luftstroms, der auf die fixierten Schaufeln (15a) trifft, erzeugen, die im Wesentlichen im Bereich zwischen 15° und 30° liegt; wobei der Kompressor (1) dadurch gekennzeichnet ist, dass jede fixierte Schaufel (15a) der Endstufe (12) einen Krümmungswinkel besitzt, der im Bereich zwischen ungefähr 45° und 60° und genauer zwischen ungefähr 48° und 54° liegt.
  2. Kompressor nach Anspruch 1, dadurch gekennzeichnet, dass der Diffusor (5) eine Anordnung von Leitschaufeln (33) umfasst.
  3. Kompressor nach Anspruch 2, dadurch gekennzeichnet, dass der Diffusor (5) einen Einlassabschnitt (29) nahe der Endstufe (12) und einen Auslassabschnitt (30), der mit einer oder mehreren Brennkammern verbunden ist, umfasst; wobei die Anordnung von Leitschaufeln (33) durch den Diffusor (5) im Wesentlichen an dem Auslassabschnitt (30) getragen wird.
  4. Kompressor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Diffusor (5) im Innern einen gekrümmten divergierenden Ringkanal (28) besitzt, dessen Querschnitt ansteigt.
  5. Kompressor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass jede fixierte Schaufel (15a) der Endstufe (12) einen Abweichungswinkel von weniger als 10° besitzt.
  6. Kompressor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass jede fixierte Schaufel (15a) der Endstufe (12) eine Eintrittskante (21), eine Austrittskante (22) gegenüber der Eintrittskante (21), eine Saugseite (23) und eine Druckseite (24) umfasst; wobei jede fixierte Schaufel (15a) so gestaltet ist, dass die lokale Schaufelbelastung in jenem Bereich der fixierten Schaufeln (15a) maximal ist, der im Wesentlichen nahe der Eintrittskante (21) ist.
  7. Kompressor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die fixierten Schaufeln (15a) der Endstufe (12) so gestaltet sind, dass sie verhindern, dass der Kompressor (1) die Grenzpumpbedingung erreicht.
EP07706234.7A 2007-01-17 2007-01-17 Mehrstufiger turbogassystemverdichter Revoked EP2126367B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL07706234T PL2126367T3 (pl) 2007-01-17 2007-01-17 Wielostopniowa sprężarka układu turbogazowego

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/IT2007/000035 WO2008087670A1 (en) 2007-01-17 2007-01-17 Turbogas system multistage compressor

Publications (2)

Publication Number Publication Date
EP2126367A1 EP2126367A1 (de) 2009-12-02
EP2126367B1 true EP2126367B1 (de) 2014-03-12

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ID=38120351

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EP07706234.7A Revoked EP2126367B1 (de) 2007-01-17 2007-01-17 Mehrstufiger turbogassystemverdichter

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EP (1) EP2126367B1 (de)
PL (1) PL2126367T3 (de)
WO (1) WO2008087670A1 (de)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114962342B (zh) * 2022-05-27 2024-04-02 哈尔滨工程大学 一种压气机端区振动结构

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4678398A (en) * 1985-05-08 1987-07-07 The Garrett Corporation High efficiency transonic mixed-flow compressor method and apparatus
US5088892A (en) * 1990-02-07 1992-02-18 United Technologies Corporation Bowed airfoil for the compression section of a rotary machine
US5249921A (en) * 1991-12-23 1993-10-05 General Electric Company Compressor outlet guide vane support
US6375419B1 (en) * 1995-06-02 2002-04-23 United Technologies Corporation Flow directing element for a turbine engine
US6439838B1 (en) * 1999-12-18 2002-08-27 General Electric Company Periodic stator airfoils
SE0004001D0 (sv) * 2000-11-02 2000-11-01 Atlas Copco Tools Ab Axial flow compressor

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PL2126367T3 (pl) 2014-07-31
WO2008087670A1 (en) 2008-07-24
EP2126367A1 (de) 2009-12-02

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