EP2132446A1 - Air intake for a gas turbine compressor - Google Patents

Air intake for a gas turbine compressor

Info

Publication number
EP2132446A1
EP2132446A1 EP07736681A EP07736681A EP2132446A1 EP 2132446 A1 EP2132446 A1 EP 2132446A1 EP 07736681 A EP07736681 A EP 07736681A EP 07736681 A EP07736681 A EP 07736681A EP 2132446 A1 EP2132446 A1 EP 2132446A1
Authority
EP
European Patent Office
Prior art keywords
air intake
baffle
compressor
foregoing
axis
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.)
Withdrawn
Application number
EP07736681A
Other languages
German (de)
French (fr)
Inventor
Lorenzo Arcangeli
Mauro Sacchetti
Stefano Traverso
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
Original Assignee
Ansaldo Nucleare SpA
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Ansaldo Nucleare SpA filed Critical Ansaldo Nucleare SpA
Publication of EP2132446A1 publication Critical patent/EP2132446A1/en
Withdrawn legal-status Critical Current

Links

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
    • F04D29/42—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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
    • F02C7/04—Air intakes for gas-turbine plants or jet-propulsion plants
    • 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
    • F04D29/441—Fluid-guiding means, e.g. diffusers 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
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/54—Fluid-guiding means, e.g. diffusers
    • F04D29/541—Specially adapted for elastic fluid pumps
    • 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
    • F04D29/545—Ducts
    • 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
    • F04D29/70—Suction grids; Strainers; Dust separation; Cleaning
    • F04D29/701—Suction grids; Strainers; Dust separation; Cleaning especially adapted for elastic fluid pumps
    • 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

Definitions

  • the present invention relates to an air intake for a compressor, in particular a power plant gas turbine compressor.
  • the air intake is located between an air filter box and a compressor, and supplies the compressor with air filtered by the air filter box.
  • Known air intakes comprise a substantially horizontal inlet portion connected to the air filter box; and a substantially vertical outlet portion connected to the inlet of the compressor substantially at an end portion of the outlet portion.
  • Air intakes of this type have several major drawbacks .
  • the airflow undergoes severe load losses substantially caused by the -formation of swirl and recirculating air regions.
  • the turbulence produced in the airflow when passing from the inlet portion to the outlet portion also produces losses in the compressor.
  • the air flowing into the compressor in fact, has severe swirl components, which result in severe load losses in the compressor, especially at the compressor inlet guide vanes (IGV) .
  • known air intakes fail to eliminate condensation, which forms on the inner surfaces of the air intake walls and may be sucked into the compressor, thus resulting in erosion damage caused by water droplets systematically impinging onto the compressor vanes.
  • Figure 1 shows a schematic view in perspective of an air intake in accordance with th present invention
  • Figure 2 shows a schematic view in perspective, with parts in section and parts removed for clarity, of a first detail of the Figure 1 air intake;
  • Figure 3 shows a section, with parts removed for clarity, of the Figure 1 air intake
  • Figure 4 shows a view in perspective, with parts removed for clarity, of a second detail of the Figure 1 air intake
  • Figure 5 shows a view in perspective, with parts in section and parts removed for clarity, of a third detail of the Figure 1 air intake;
  • Figure 6 shows a view in perspective, with parts in section and parts removed for clarity, of a fourth detail of the Figure 1 air intake.
  • FIG. 1 indicates an air intake for a compressor 2 of a power plant (not shown) , in particular a gas turbine plant.
  • Air intake 1 is substantially located between compressor 2 and an air filter box 3.
  • Compressor 2 is preferably a multistage, axial compressor extending along an axis A.
  • Figure 1 simply shows an inner inlet portion of compressor 2 comprising guide spokes 4 and inlet guide vanes (IGV) 5.
  • Air intake 1 comprises a front wall 6 facing compressor 2 in use, a rear wall 7 opposite front wall 6, two lateral walls 8, and a bottom wall 9, which define a channel 10 (Figure 3) inside which filtered air from air filter box 3 flows to supply compressor 2. More specifically, air intake 1 comprises an inlet portion 11 connected to air filter box 3 and extending substantially along a horizontal axis B parallel to axis A of compressor 2; a connecting portion 12 with curved parts; and an outlet portion 13 extending substantially vertically along an axis C perpendicular to axis B. Connecting portion 12, in which rear wall 7 is curved, connects inlet portion 11 and outlet portion 13, where rear wall 7 is flat. More specifically, connecting portion 12 is bounded by a first section S facing inlet portion 11, and by a second section S' facing outlet portion 13.
  • An outlet section 14 is connected substantially to one end of outlet portion 13.
  • air intake 1 comprises a first and second baffle 17, 18 inside connecting portion 12.
  • first and second baffle 17, 18 extend parallel to each other between the two lateral walls 8 of air intake 1 and in a direction substantially perpendicular to both axis B of inlet portion 11 and axis C of outlet portion 13, and are designed to divert the airflow from air filter box 3 and minimize the formation of swirl components when passing from inlet portion 11 to outlet portion 13.
  • rear wall 7 has a constant radius of curvature R, preferably of about 200 mm.
  • a point P located along rear wall 7 at first section S, is separated from front wall 6 by a distance D measured parallel to axis B of
  • First baffle 17 comprises a flat trailing portion 17a extending up to second section S 1 and of a height equal to radius of curvature R; and a substantially cylindrical leading portion 17b of a radius equal to twice radius of curvature R.
  • the distance, along second section S', between trailing portion 17a and rear wall 7 is roughly one ninth of distance D.
  • Second baffle 18 comprises a flat trailing portion 18a extending up to second section S 1 and of a height equal to radius of curvature R; and a substantially cylindrical leading portion 18b of a radius equal to five times radius of curvature R.
  • the distance between trailing portion 17a of first baffle 17 and trailing portion 18a of second baffle 18 equals roughly 2/5 of distance D.
  • First and second baffle 17, 18 are preferably about 3 mm thick, whereas front wall 6, rear wall 7, and bottom wall 9 are preferably about 5 mm thick.
  • outlet portion 13 of air intake 1 comprises a flow guide 19, in turn comprising two metal leaf portions 20 shaped to direct the airflow, not drawn by compressor 2, from bottom wall 9 back to outlet section 14 (as shown by the arrows in Figure 4).
  • Each metal leaf portion 20 is shaped to form a curve with a constant radius of curvature, preferably of about 150 cm, and has a first end 21 fixed to bottom wall 9; and a second end 22 fixed to a partition wall 24 so that the concavity of the curve faces upwards.
  • Partition wall 24 extends from substantially the mid-point of bottom wall 9 to outlet section 14 of air intake 1 in a direction substantially perpendicular to bottom wall 9 and generally parallel to axis C.
  • metal leaf portions 20 prevents mixing of the airflow close to bottom wall 9, which could give rise to swirl and, as stated, load losses in compressor 2.
  • each metal leaf portion 20 comprises a groove 25 crosswise to metal leaf portion 20 and having a number of drain holes 26.
  • Drain holes 26 assist in disposing of condensation formed on the inner surfaces of air intake 1, and prevent it from settling on bottom wall 9 by means of a drain system (not shown) on bottom wall 9.
  • Flow guide 19 also comprises two plates 29 located at two edges 30 formed by bottom wall 9 and respective lateral walls 8. Plates 29 are substantially curved to reduce the formation of swirl and direct the airflow onto sheet metal portions 20.
  • flow guide 19 is formed in one appropriately shaped piece.
  • bottom wall 9 is shaped to define flow guide 19.
  • air intake 1 also comprises a first and second substantially circular channel 31, 32 for collecting condensation formed inside air intake 1, in particular on front wall 6 and rear wall
  • first channel 31 extends in the form of a collar about outlet section 14, and comprises a C-section sheet fixed in an inner circle of front wall ⁇ , so that condensation is collected, diverted about outlet section 14, and drained onto bottom wall 9 where it flows out through drain holes 26.
  • Second channel 32 extends about a truncated cone 33 located at the inlet of compressor 2, and which is inserted inside air intake 1 through outlet section 14 and contacts rear wall 7.
  • baffles 17 and 18 minimize load losses caused by the formation of swirl when passing from predominantly horizontal flow to predominantly vertical flow.
  • flow guide 19 assists in reducing turbulence in the airflow, thus reducing anomalous flow components with respect to the compressor IGV design direction, and so reducing load losses within the compressor and increasing power output.
  • condensation channels 31 and 32 provide for channeling condensation, formed on the surfaces of front, rear, and lateral walls 6, 7, 8 facing channel 10, substantially onto bottom wall 9, where it is disposed of by drain holes 26.

Abstract

An air intake (1) for a compressor (2) has an inlet portion (11) for drawing in outside air, the inlet portion (11) extending along a first axis (B); an outlet portion (13) for feeding the aspirated air to the compressor (2), the outlet portion (13) extending along a second axis (C) not aligned with the first axis (B); and a connecting portion (12) connecting the inlet portion (11) to the outlet portion (13); the air intake (1) also has at least a first baffle (17; 18) housed inside the air intake (1) to divert airflow from the inlet portion (11) to the outlet portion (13).

Description

AIR INTAKE FOR A GAS TURBINE COMPRESSOR
TECHNICAL FIELD The present invention relates to an air intake for a compressor, in particular a power plant gas turbine compressor.
BACKGROUND ART
In known power plants, the air intake is located between an air filter box and a compressor, and supplies the compressor with air filtered by the air filter box.
Known air intakes comprise a substantially horizontal inlet portion connected to the air filter box; and a substantially vertical outlet portion connected to the inlet of the compressor substantially at an end portion of the outlet portion.
The air filtered by the air filter box therefore flows along the whole of the inlet portion . and along large part of the outlet portion into the compressor. Air intakes of this type have several major drawbacks .
In particular, as it passes from a predominantly horizontal flow configuration (along the inlet portion) to a predominantly vertical flow configuration (along the outlet portion) , the airflow undergoes severe load losses substantially caused by the -formation of swirl and recirculating air regions. The turbulence produced in the airflow when passing from the inlet portion to the outlet portion also produces losses in the compressor. The air flowing into the compressor, in fact, has severe swirl components, which result in severe load losses in the compressor, especially at the compressor inlet guide vanes (IGV) .
Moreover, known air intakes fail to eliminate condensation, which forms on the inner surfaces of the air intake walls and may be sucked into the compressor, thus resulting in erosion damage caused by water droplets systematically impinging onto the compressor vanes.
DISCLOSURE OF INVENTION
It is an object of the present invention to provide a gas turbine compressor air intake designed to eliminate the aforementioned drawbacks of the known art. More specifically, it is an object of the invention to provide a gas turbine compressor air intake designed to minimize load losses in the airflow, and which at the same time is cheap and easy to implement .
According to the present invention, there is provided a gas turbine compressor air intake as claimed in Claim 1.
BRIEF DESCRIPTION OF THE DRAWINGS
A non-limiting embodiment of the present invention will be described by way of example with reference to the accompanying drawings, in which:
Figure 1 shows a schematic view in perspective of an air intake in accordance with th present invention; Figure 2 shows a schematic view in perspective, with parts in section and parts removed for clarity, of a first detail of the Figure 1 air intake;
Figure 3 shows a section, with parts removed for clarity, of the Figure 1 air intake; Figure 4 shows a view in perspective, with parts removed for clarity, of a second detail of the Figure 1 air intake;
Figure 5 shows a view in perspective, with parts in section and parts removed for clarity, of a third detail of the Figure 1 air intake;
Figure 6 shows a view in perspective, with parts in section and parts removed for clarity, of a fourth detail of the Figure 1 air intake.
BEST MODE FOR CARRYING OUT THE INVENTION Number 1 in Figure 1 indicates an air intake for a compressor 2 of a power plant (not shown) , in particular a gas turbine plant. Air intake 1 is substantially located between compressor 2 and an air filter box 3. Compressor 2 is preferably a multistage, axial compressor extending along an axis A. And Figure 1 simply shows an inner inlet portion of compressor 2 comprising guide spokes 4 and inlet guide vanes (IGV) 5.
Air intake 1 comprises a front wall 6 facing compressor 2 in use, a rear wall 7 opposite front wall 6, two lateral walls 8, and a bottom wall 9, which define a channel 10 (Figure 3) inside which filtered air from air filter box 3 flows to supply compressor 2. More specifically, air intake 1 comprises an inlet portion 11 connected to air filter box 3 and extending substantially along a horizontal axis B parallel to axis A of compressor 2; a connecting portion 12 with curved parts; and an outlet portion 13 extending substantially vertically along an axis C perpendicular to axis B. Connecting portion 12, in which rear wall 7 is curved, connects inlet portion 11 and outlet portion 13, where rear wall 7 is flat. More specifically, connecting portion 12 is bounded by a first section S facing inlet portion 11, and by a second section S' facing outlet portion 13.
An outlet section 14 is connected substantially to one end of outlet portion 13.
With reference to Figure 2, air intake 1 comprises a first and second baffle 17, 18 inside connecting portion 12.
More specifically, first and second baffle 17, 18 extend parallel to each other between the two lateral walls 8 of air intake 1 and in a direction substantially perpendicular to both axis B of inlet portion 11 and axis C of outlet portion 13, and are designed to divert the airflow from air filter box 3 and minimize the formation of swirl components when passing from inlet portion 11 to outlet portion 13.
With reference to Figure 3, in connecting portion 12, rear wall 7 has a constant radius of curvature R, preferably of about 200 mm. A point P, located along rear wall 7 at first section S, is separated from front wall 6 by a distance D measured parallel to axis B of
(horizontal) inlet portion 11. In other words, distance D equals radius of curvature R plus a width D1 of second section S' (also measured parallel to axis B) . First baffle 17 comprises a flat trailing portion 17a extending up to second section S1 and of a height equal to radius of curvature R; and a substantially cylindrical leading portion 17b of a radius equal to twice radius of curvature R. The distance, along second section S', between trailing portion 17a and rear wall 7 is roughly one ninth of distance D.
Second baffle 18 comprises a flat trailing portion 18a extending up to second section S1 and of a height equal to radius of curvature R; and a substantially cylindrical leading portion 18b of a radius equal to five times radius of curvature R. The distance between trailing portion 17a of first baffle 17 and trailing portion 18a of second baffle 18 equals roughly 2/5 of distance D. First and second baffle 17, 18 are preferably about 3 mm thick, whereas front wall 6, rear wall 7, and bottom wall 9 are preferably about 5 mm thick.
With reference to Figure 4, outlet portion 13 of air intake 1 comprises a flow guide 19, in turn comprising two metal leaf portions 20 shaped to direct the airflow, not drawn by compressor 2, from bottom wall 9 back to outlet section 14 (as shown by the arrows in Figure 4). Each metal leaf portion 20 is shaped to form a curve with a constant radius of curvature, preferably of about 150 cm, and has a first end 21 fixed to bottom wall 9; and a second end 22 fixed to a partition wall 24 so that the concavity of the curve faces upwards. Partition wall 24 extends from substantially the mid-point of bottom wall 9 to outlet section 14 of air intake 1 in a direction substantially perpendicular to bottom wall 9 and generally parallel to axis C.
The above configuration of metal leaf portions 20 prevents mixing of the airflow close to bottom wall 9, which could give rise to swirl and, as stated, load losses in compressor 2.
With reference to Figure 5, close to first end 21, each metal leaf portion 20 comprises a groove 25 crosswise to metal leaf portion 20 and having a number of drain holes 26.
Drain holes 26 assist in disposing of condensation formed on the inner surfaces of air intake 1, and prevent it from settling on bottom wall 9 by means of a drain system (not shown) on bottom wall 9.
Flow guide 19 also comprises two plates 29 located at two edges 30 formed by bottom wall 9 and respective lateral walls 8. Plates 29 are substantially curved to reduce the formation of swirl and direct the airflow onto sheet metal portions 20.
In an alternative embodiment of the present invention, flow guide 19 is formed in one appropriately shaped piece.
In a further alternative embodiment, bottom wall 9 is shaped to define flow guide 19.
With reference to Figure 6, air intake 1 also comprises a first and second substantially circular channel 31, 32 for collecting condensation formed inside air intake 1, in particular on front wall 6 and rear wall
7.
More specifically, first channel 31 extends in the form of a collar about outlet section 14, and comprises a C-section sheet fixed in an inner circle of front wall β, so that condensation is collected, diverted about outlet section 14, and drained onto bottom wall 9 where it flows out through drain holes 26.
Second channel 32 extends about a truncated cone 33 located at the inlet of compressor 2, and which is inserted inside air intake 1 through outlet section 14 and contacts rear wall 7.
The air intake according to the present invention has the following advantages . Firstly, baffles 17 and 18 minimize load losses caused by the formation of swirl when passing from predominantly horizontal flow to predominantly vertical flow. Secondly, flow guide 19 assists in reducing turbulence in the airflow, thus reducing anomalous flow components with respect to the compressor IGV design direction, and so reducing load losses within the compressor and increasing power output.
Finally, condensation channels 31 and 32 provide for channeling condensation, formed on the surfaces of front, rear, and lateral walls 6, 7, 8 facing channel 10, substantially onto bottom wall 9, where it is disposed of by drain holes 26.
Clearly, changes may be made to the compressor air intake as described and illustrated herein without, however, departing from the scope of the accompanying Claims .

Claims

1) An air intake (1) for a compressor (2), comprising: an inlet portion (11) for drawing in outside air, the inlet portion (11) extending along a first axis (B) ; an outlet portion (13) for feeding the aspirated air to the compressor (2), the outlet portion (13) extending along a second axis (C) not aligned with the first axis (B) ; and a connecting portion (12) connecting the inlet portion (11) to the outlet portion (13); the air intake (1) being characterized by comprising at least a first baffle (17; 18) housed inside the air intake (1) to divert airflow from the inlet portion (11) to the outlet portion (13) .
2) An air intake as claimed in Claim 1, characterized in that the second axis (C) is substantially perpendicular to the first axis (B) .
3) An air intake as claimed in any one of the foregoing Claims, characterized in that the first axis (B) is substantially horizontal, and the second axis (C) is substantially vertical.
4) An air intake as claimed in any one of the foregoing Claims, characterized in that the first baffle (17; 18) extends, inside the air intake (1), substantially in a direction perpendicular to the first axis (B) .
5) An air intake as claimed in any one of the foregoing Claims, characterized in that the first baffle (17; 18) extends, inside the air intake (1), substantially in a direction perpendicular to the second axis (C) .
6) An air intake as claimed in any one of the foregoing Claims, characterized by comprising a front wall (6) facing the compressor (2) in use; a rear wall
(7) opposite the front wall (6); and two lateral walls (8); the first baffle (17; 18) extending between the two lateral walls (8) of the air intake (1) .
7) An air intake as claimed in any one of the foregoing Claims, characterized in that the first baffle (17; 18) is located inside the connecting portion (12) . 8) An air intake as claimed in any one of the foregoing Claims, characterized in that the first baffle (17; 18) has a concavity facing the inlet portion (11).
9) An air intake as claimed in any one of the foregoing Claims, characterized by comprising a second baffle (18; 17) housed inside the air intake (1), substantially at the connecting portion (12), to divert airflow from the inlet portion (11) to the outlet portion (13).
10) An air intake as claimed in Claim 9, characterized in that the second baffle (18; 17) extends parallel to the first baffle (17; 18).
11) An air intake as claimed in Claim 9 or 10, characterized in that the second baffle (18; 17) has a concavity facing the first baffle (17; 18) .
12) An air intake as claimed in any one of Claims 9 to 11, characterized in that the first and second baffle (17, 18) are about 3 mm thick. 13) An air intake as claimed in any one of the foregoing Claims, characterized in that the outlet portion (13) comprises an outlet section (14) ; and a flow guide (19) shaped to direct airflow from a bottom wall (9) of the outlet portion (13) to the outlet section (14) .
14) An air intake as claimed in Claim 13, characterized in that the flow guide (19) is formed in one piece.
15) An air intake as claimed in Claim 13 or 14, characterized in that the flow guide (19) is integrated in the bottom wall (9) .
16) An air intake as claimed in any one of Claims 13 to 15, characterized in that the flow guide (19) comprises two metal leaf portions (20) located substantially at the outlet portion (13) .
17) An air intake as claimed in Claim 16, characterized in that each metal leaf portion (20) is shaped to form a curve with a constant radius of curvature; the metal leaf portions (20) being located side by side.
18) An air intake as claimed in Claim 16 or 17, characterized in that each metal leaf portion (20) has a first end (21) fixed to the bottom wall (9) of the air intake (1) ; said first end (21) having a groove (25) substantially crosswise to the metal leaf portion (20) and having condensation drain holes (26) .
19) An air intake as claimed in any one of Claims 16 to 18, characterized in that each metal leaf portion (20) comprises a second end (22) fixed to a partition wall (24); the partition wall (24) extending from the bottom wall (9) , substantially from a mid-point of the bottom wall (9) , and in a direction substantially perpendicular to the bottom wall (9) .
20) An air intake as claimed in any one of Claims 13 to 19, characterized in that the flow guide (19) comprises two substantially curved plates (29) located at two edges (30), each formed by the bottom wall (9) and by a respective lateral wall (8).
21) An air intake as claimed in any one of the foregoing Claims, characterized in that the outlet portion (13) comprises an outlet section (14) ; the air intake (1) comprising a substantially C-section first channel (31) extending about the outlet section (14) .
22) An air intake as claimed in any one of the foregoing Claims, characterized by comprising a substantially C-section second channel (32) extending about a truncated cone (33) located at the inlet of the compressor (2) and connected to the air intake (1) .
23) An axial compressor comprising an air intake (1) as claimed in any one of the foregoing Claims.
24) A gas turbine power plant comprising an air filter box (3) ; a compressor (2) ; and an air intake (1) connected to the air filter box (3) and to the compressor (2) to supply filtered air from the air filter box (3) to the compressor (2) ; the plant being characterized in that the air intake (1) is as claimed in any one of Claims 1 to 22.
EP07736681A 2007-03-09 2007-03-09 Air intake for a gas turbine compressor Withdrawn EP2132446A1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/IT2007/000176 WO2008111098A1 (en) 2007-03-09 2007-03-09 Air intake for a gas turbine compressor

Publications (1)

Publication Number Publication Date
EP2132446A1 true EP2132446A1 (en) 2009-12-16

Family

ID=38763529

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07736681A Withdrawn EP2132446A1 (en) 2007-03-09 2007-03-09 Air intake for a gas turbine compressor

Country Status (3)

Country Link
EP (1) EP2132446A1 (en)
RU (1) RU2443880C2 (en)
WO (1) WO2008111098A1 (en)

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JP5707948B2 (en) * 2011-01-12 2015-04-30 株式会社豊田自動織機 Air compressor
US9217369B2 (en) * 2012-03-15 2015-12-22 Siemens Aktiengesellschaft Compressor inlet manifold for a gas turbine engine
FR3007798A1 (en) * 2013-06-28 2015-01-02 Eurocopter France TURBOMOTEUR PLENUM, AND AIRCRAFT
RU190525U1 (en) * 2018-11-16 2019-07-03 Публичное акционерное общество "МОТОР СИЧ" INPUT DEVICE CENTRIFUGAL COMPRESSOR
EP3936710B1 (en) * 2020-07-06 2023-04-12 ANSALDO ENERGIA S.p.A. Air intake for a stationary gas turbine engine

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Also Published As

Publication number Publication date
WO2008111098A1 (en) 2008-09-18
WO2008111098A8 (en) 2009-10-29
RU2443880C2 (en) 2012-02-27
RU2009137392A (en) 2011-04-20

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