EP2978977A1 - Radial or mixed-flow compressor diffuser having vanes - Google Patents
Radial or mixed-flow compressor diffuser having vanesInfo
- Publication number
- EP2978977A1 EP2978977A1 EP14718669.6A EP14718669A EP2978977A1 EP 2978977 A1 EP2978977 A1 EP 2978977A1 EP 14718669 A EP14718669 A EP 14718669A EP 2978977 A1 EP2978977 A1 EP 2978977A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- leading edge
- diffuser
- radial
- trailing edge
- rope
- 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.)
- Granted
Links
- 239000007789 gas Substances 0.000 description 16
- 238000009792 diffusion process Methods 0.000 description 6
- 239000012530 fluid Substances 0.000 description 5
- 238000005086 pumping Methods 0.000 description 5
- 230000003068 static effect Effects 0.000 description 5
- 230000000694 effects Effects 0.000 description 3
- 238000011144 upstream manufacturing Methods 0.000 description 3
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 230000000903 blocking effect Effects 0.000 description 1
- 238000007664 blowing Methods 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 239000000470 constituent Substances 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
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
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
- F04D29/444—Bladed diffusers
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/08—Centrifugal pumps
- F04D17/10—Centrifugal pumps for compressing or evacuating
- F04D17/12—Multi-stage 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
- F05D2250/52—Outlet
Definitions
- the invention generally relates to gas turbine engines, and more particularly to a diffusion stage of a radial or mixed compressor of a gas turbine, as well as to an associated compressor.
- a compressor comprises one or more rotating disks (rotor or wheel), bladed or not and one or more fixed vane wheels (rectifier stages).
- a radial (or centrifugal) compressor has at least one radial compression stage, that is to say capable of producing a flow of gas perpendicular to the central axis of the compressor. It comprises at least one radial impeller which sucks the air axially, which, under the effect of the radial force, is accelerated, compressed and discharged radially. This air is then straightened in a diffuser (fixed blade) which transforms part of its speed into static pressure by slowing the gases at the exit of the wheel. The operation must take place with a minimum of total pressure loss while maintaining a satisfactory compressor stability level in order to maintain an acceptable pumping margin for the operation of the turbomachine.
- the gases are then guided to the combustion chamber.
- a mixed compressor (or helico-radial) has at least one compression stage inclined with respect to said central axis, so that the fluid leaves the compressor impeller at a non-zero angle with the radial direction.
- a diffuser of a radial compressor is composed of a wheel formed of two flanges between which the gases flow radially or inclined from the center to the periphery.
- the fins are distributed between the flanges along the wheel. These fins form a flow grid between the leading edges of these fins and the trailing edges.
- the deflection of the air flow at the exit of the impeller by the fins of the diffuser can cause a detachment of the fluid on the lower surface or the upper surface of the fins, which detachment, as long as it is important, can lead to the stall. fluid and, consequently, pumping. It is known that this pumping phenomenon is harmful to the constituent elements of the compressor, so that we try to avoid it as far as possible.
- the vanes of the diffuser are constructed from a lower surface and an extrados wall in the shape of a circular arc, and comprise a quasi-linear angle law.
- An example of such a fin is illustrated in FIG.
- these fins have a limitation in terms of diffusing capacity. Indeed, an increase in the diffusion by these fins causes a drop in isentropic efficiency and an increase in the instability of the compressor.
- An object of the invention is to improve the performance and pumping margin of diffusers of radial and mixed compressors of the prior art.
- the invention aims to provide a diffuser of a radial or mixed compressor capable of limiting the fall of the isentropic efficiency of the compressor and improve the ability to slow down and straighten the flow delivered by the impeller of the compressor while maintaining the stability of this flow.
- the invention proposes a fin of a diffuser for a radial or mixed compressor of a motor, comprising a leading edge disposed opposite a gas flow, a trailing edge opposite the leading edge. , a lower side wall and an extrados side wall which connect the leading edge to the trailing edge.
- the fin profile includes a camber line having at least two points of inflection between the leading edge and the trailing edge. The curvature of the intrados wall and the curvature of the extrados wall also substantially follow the curvature of the camber line, so that:
- the intrados wall comprises, between the leading edge and the trailing edge, at least two convex parts separated by a concave part, and
- the upper surface comprises, between the leading edge and the trailing edge, at least two concave parts separated by a convex part, and the profile defines a rope which extends between the leading edge and the edge; leakage, and the convex portions of the intrados wall and the concave portions of the extrados wall extend at least partially on the same side of said rope.
- the invention also proposes a diffuser comprising at least one fin as described above, as well as a radial or mixed compressor comprising such a diffuser, and an engine comprising such a compressor.
- FIG. 1 illustrates an example of blade profile of a diffuser according to the prior art
- FIG. 2 illustrates an example of blade profile of a diffuser according to the invention
- FIG. 3 is a detailed view of a blade of FIG. 2, on which a rope and a median line of the blade have been represented, and
- FIG. 4 illustrates an example of an engine that can comprise a diffuser according to the invention.
- a radial diffuser according to the present invention is particularly intended to be used with a compressor 2 of radial or mixed type.
- FIG. 4 is a partial sectional view of a motor 1 comprising a radial compressor 2.
- a gas flow F is first drawn into an air inlet sleeve and then compressed between the blades 3a of a compressor wheel 3 radial 2 and its housing.
- the compressor 2 is of axial symmetry around an axis X.
- the compressed gas flow F then exits radially from the wheel 3. If the compressor 2 was mixed, the gas flow would exit inclined at a non-zero angle with respect to a radial direction to the X axis.
- the compressed air leaves the wheel 3 radially while having a kinetic moment and passes through a diffuser 5.
- the role of the diffuser 5 is to convert a portion of the kinetic energy of the gas from the compressor 2 in static pressure by slowing the speed of gases, and straighten the flow from the wheel 3. It comprises for this a plurality of fins 10 arranged along its circumference, which extend between a front flange 5a and a rear flange 5b.
- Each of the fins 10 has, in known manner, a leading edge 1 1 arranged opposite a gas flow, a trailing edge 12 opposite to the leading edge 1 1, an extrados side wall 13 and a side wall 14 that connect the leading edge 1 1 to the trailing edge 12.
- the front flanges 5a and rear 5b may be planar.
- at least one of the flanges 5a, 5b may comprise, in the space they define between them, at least one zone with alternating curvature between two fins 10, so that the air stream may comprise evolutionary head and foot meridians.
- the flanges 5a, 5b may be evolutionary shapes axisymmetric.
- front flanges 5a and 5b rear can be arranged to allow suction and blowing into the diffuser 5.
- At least one of the fins 10 of the diffuser 5, preferably all of the fins 10, comprises, from upstream to downstream in the direction of the gas flow:
- a first so-called capture zone whose shape is configured to adapt to the upstream flow
- the fin 10 comprises a profile whose camber line 15 has at least two points of inflection 11, 12 between its leading edge 11 and its trailing edge 12, that is to say at least two changes of concavity.
- the inflection points 11, 12 together define the capture zone, which comprises the portion of the fin 10 extending upstream of the first point of inflection 11, of the diffusion zone, which comprises the part of the fin 10 extending downstream of the second point of inflection 12.
- the inflection points 11, 12 are situated between 10% and 90% of the cord 16, preferably between 30% and 70%. %.
- a first 11 of the inflection points may be between 35% and 55% of the cord 16, while the second inflection point 12 is between 55% and 65% of the cord 16.
- the inflection 11, 12 may be arranged symmetrically with respect to the center of the rope 16.
- the profile of the fin 10 may comprise more points of inflection 11, 12.
- the camber line 15 presents successively at least, between the leading edge 1 1 and the trailing edge 12, a first concavity, a second concavity different from the first concavity, then a third concavity.
- the points of inflection 11, 12 are symmetrical relative to the center of the rope 16, the second concavity is then centered in the fin 10.
- the intrados wall 14 and the extrados wall 13 substantially follow the curvature of the camber line 15, and therefore have as many points of inflection 11, 12.
- the intrados wall 14 and the extrados wall 13 therefore comprise two inflection points 11, 12.
- the intrados wall 14 comprises a convex portion 14 a between the leading edge 11 and the first point of inflection, then a concave portion 14b between the two points of inflection 11, 12, and a convex portion 14c between the second point of inflection and the trailing edge 12.
- the upper surface 13 as for it comprises a concave part 13a between the leading edge 1 1 and the first point of inflection, then a convex part 13b between the two points of inflection 11, 12, and then a concave part 13c between the second inflection point and the trailing edge 12.
- camber line 15 extends between the intrados wall 14 and the rope 16.
- the line of camber 15 and the intrados wall 14 extend away from the rope 16.
- the concave areas of the upper wall 13 pass through the rope 16, and are therefore at least partially on the same side as the line of camber 15 of said rope 16.
- the leading edge 11 and the trailing edge 12 are oriented in the same general direction with respect to the flow. gases that are usually encountered in conventional diffusers, thereby preserving the neck section, i.e., the fluid inlet section between two adjacent fins. In this way, the stability of the diffuser 5 is maintained while improving the diffusion of the flow.
- the angle of attack ⁇ (which corresponds to the angle between the tangent to the camber line 15 at the leading edge 11 and the rope 16) may be substantially identical to that of the conventional fins. For example, the angle of attack may be between about 0 ° and about 45 °.
- the presence of the second inflection point 12 makes it possible to modify the shape of the fins 10 in their diffusion zone to increase the efficiency of the diffuser 5, without modifying the shape of the capture zone. Indeed, it is now possible to increase the angle between the camber line 15 at the trailing edge 12 and the rope 16, regardless of the shape of the capture area, which allows to straighten more strongly. the flow of gases and therefore increase the static pressure and the total pressure ratio iso-heating output of the diffuser 5, and thus improve the isentropic efficiency of the diffuser 5 while maintaining the margin pumping and therefore the stability compressor 2.
- the camber line 15 of the fin profile 10 comprises at least two inflection points 11, 12.
- the number of inflection points 11, 12 can be even in order to maintain the orientation. general of the leading edge 1 1 and the trailing edge 12 relative to the flow, and thus to preserve section at the neck.
- the corresponding camber line 15 again extends between the intrados wall 14 and the rope 16, so that at any point between the leading edge 11 and the edge 12, the camber line 15 and the intrados wall 14 extend at a distance from the rope 16, and the concave zones of the extrados wall 13 pass through the rope 16.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR1352829A FR3003908B1 (en) | 2013-03-28 | 2013-03-28 | DIFFUSER WITH FINES OF A RADIAL OR MIXED COMPRESSOR |
PCT/FR2014/050693 WO2014154997A1 (en) | 2013-03-28 | 2014-03-25 | Radial or mixed-flow compressor diffuser having vanes |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2978977A1 true EP2978977A1 (en) | 2016-02-03 |
EP2978977B1 EP2978977B1 (en) | 2016-10-19 |
Family
ID=48901098
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP14718669.6A Active EP2978977B1 (en) | 2013-03-28 | 2014-03-25 | Vane for radial or mixed-flow compressor |
Country Status (11)
Country | Link |
---|---|
US (1) | US9890792B2 (en) |
EP (1) | EP2978977B1 (en) |
JP (1) | JP6367917B2 (en) |
KR (1) | KR102196815B1 (en) |
CN (1) | CN105247223B (en) |
CA (1) | CA2908081C (en) |
ES (1) | ES2606831T3 (en) |
FR (1) | FR3003908B1 (en) |
PL (1) | PL2978977T3 (en) |
RU (1) | RU2651905C2 (en) |
WO (1) | WO2014154997A1 (en) |
Families Citing this family (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102014221362A1 (en) | 2014-10-21 | 2016-04-21 | Siemens Aktiengesellschaft | Profiling of vanes of nozzles in turbomachinery, in particular compressors |
DE102015107907A1 (en) * | 2015-05-20 | 2016-11-24 | Ebm-Papst Mulfingen Gmbh & Co. Kg | Eben Strömungsleitgitter |
US9732775B2 (en) * | 2015-06-24 | 2017-08-15 | The Boeing Company | Flow straightener apparatus and systems for ducted air |
KR101848437B1 (en) * | 2017-03-28 | 2018-04-13 | 한국과학기술연구원 | Centrifugal turbo machinery having flexibly variable diffuser vane |
KR102083168B1 (en) * | 2017-11-07 | 2020-03-02 | 주식회사 에어로네트 | Impeller having primary blades and secondary blades |
KR102427392B1 (en) * | 2018-01-24 | 2022-07-29 | 한화에어로스페이스 주식회사 | Diffuser for compressor |
US11421708B2 (en) | 2018-03-16 | 2022-08-23 | Carrier Corporation | Refrigeration system mixed-flow compressor |
KR102095835B1 (en) | 2019-01-25 | 2020-04-01 | (주)대주기계 | Industrial diffuser with a wavy rotating cylinder |
US10989219B2 (en) | 2019-02-04 | 2021-04-27 | Honeywell International Inc. | Diffuser assemblies for compression systems |
US11098730B2 (en) * | 2019-04-12 | 2021-08-24 | Rolls-Royce Corporation | Deswirler assembly for a centrifugal compressor |
CN112651117B (en) * | 2020-12-21 | 2023-03-28 | 贵州电网有限责任公司 | Dynamic segmental closing method for guide vane of hydroelectric generating set |
CN113339267B (en) * | 2021-06-17 | 2022-07-26 | 清华大学 | Cambered high-energy-density blade design method and vane pump designed by same |
Family Cites Families (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3298636A (en) * | 1965-01-15 | 1967-01-17 | Arnholdt Eric | Airfoil |
SU1409785A2 (en) * | 1986-12-23 | 1988-07-15 | Университет дружбы народов им.Патриса Лумумбы | Vaned diffusor of centrifugal compressor |
US5395071A (en) * | 1993-09-09 | 1995-03-07 | Felix; Frederick L. | Airfoil with bicambered surface |
JP3948785B2 (en) * | 1996-05-17 | 2007-07-25 | カルソニックカンセイ株式会社 | Centrifugal multiblade fan |
FR2937385B1 (en) * | 2008-10-17 | 2010-12-10 | Turbomeca | DIFFUSER WITH AUBES A ORIFICES |
CN101865145B (en) * | 2009-04-20 | 2012-09-19 | 日立空调·家用电器株式会社 | Electric blower, electric dust collector carrying the same and manufacturing method thereof |
EP2299124A1 (en) * | 2009-09-04 | 2011-03-23 | Siemens Aktiengesellschaft | Rotor blade for an axial compressor |
FR2958967B1 (en) * | 2010-04-14 | 2013-03-15 | Turbomeca | METHOD FOR ADJUSTING TURBOMACHINE AIR FLOW WITH CENTRIFUGAL COMPRESSOR AND DIFFUSER THEREFOR |
JP5299354B2 (en) * | 2010-06-01 | 2013-09-25 | 株式会社日立プラントテクノロジー | Turbo fluid machine |
US8834104B2 (en) * | 2010-06-25 | 2014-09-16 | Honeywell International Inc. | Vanes for directing exhaust to a turbine wheel |
US20130224004A1 (en) * | 2010-08-12 | 2013-08-29 | Sen Radhakrishnan | Radial Diffuser Vane for Centrifugal Compressors |
FR2976633B1 (en) | 2011-06-20 | 2015-01-09 | Turbomeca | METHOD OF DIFFUSING A COMPRESSION STAGE OF A GAS TURBINE AND THE DIFFUSION STAGE THEREFOR |
-
2013
- 2013-03-28 FR FR1352829A patent/FR3003908B1/en active Active
-
2014
- 2014-03-25 US US14/780,881 patent/US9890792B2/en active Active
- 2014-03-25 JP JP2016504723A patent/JP6367917B2/en not_active Expired - Fee Related
- 2014-03-25 CN CN201480030172.1A patent/CN105247223B/en not_active Expired - Fee Related
- 2014-03-25 CA CA2908081A patent/CA2908081C/en active Active
- 2014-03-25 WO PCT/FR2014/050693 patent/WO2014154997A1/en active Application Filing
- 2014-03-25 EP EP14718669.6A patent/EP2978977B1/en active Active
- 2014-03-25 PL PL14718669T patent/PL2978977T3/en unknown
- 2014-03-25 ES ES14718669.6T patent/ES2606831T3/en active Active
- 2014-03-25 RU RU2015146262A patent/RU2651905C2/en active
- 2014-03-25 KR KR1020157030921A patent/KR102196815B1/en active IP Right Grant
Also Published As
Publication number | Publication date |
---|---|
FR3003908A1 (en) | 2014-10-03 |
CA2908081A1 (en) | 2014-10-02 |
JP2016514791A (en) | 2016-05-23 |
CN105247223B (en) | 2017-05-17 |
EP2978977B1 (en) | 2016-10-19 |
ES2606831T3 (en) | 2017-03-28 |
PL2978977T3 (en) | 2017-02-28 |
CN105247223A (en) | 2016-01-13 |
FR3003908B1 (en) | 2017-07-07 |
RU2015146262A (en) | 2017-05-04 |
WO2014154997A1 (en) | 2014-10-02 |
KR20150138291A (en) | 2015-12-09 |
US9890792B2 (en) | 2018-02-13 |
KR102196815B1 (en) | 2020-12-30 |
RU2651905C2 (en) | 2018-04-24 |
RU2015146262A3 (en) | 2018-03-01 |
JP6367917B2 (en) | 2018-08-01 |
CA2908081C (en) | 2020-11-24 |
US20160053774A1 (en) | 2016-02-25 |
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