EP1774179A1 - Aube de compresseur et fabrication et utilisation d'une aube de compresseur - Google Patents

Aube de compresseur et fabrication et utilisation d'une aube de compresseur

Info

Publication number
EP1774179A1
EP1774179A1 EP05767976A EP05767976A EP1774179A1 EP 1774179 A1 EP1774179 A1 EP 1774179A1 EP 05767976 A EP05767976 A EP 05767976A EP 05767976 A EP05767976 A EP 05767976A EP 1774179 A1 EP1774179 A1 EP 1774179A1
Authority
EP
European Patent Office
Prior art keywords
blade
profile
compressor
sealing lip
side wall
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
Application number
EP05767976A
Other languages
German (de)
English (en)
Other versions
EP1774179B1 (fr
Inventor
Christian Cornelius
Bernhard Küsters
Stephan Mais
Andreas Peters
Achim Schirrmacher
Lutz Stephan
Bernd Van Den Toom
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.)
Siemens AG
Original Assignee
Siemens AG
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 Siemens AG filed Critical Siemens AG
Priority to EP05767976A priority Critical patent/EP1774179B1/fr
Priority to PL05767976T priority patent/PL1774179T3/pl
Publication of EP1774179A1 publication Critical patent/EP1774179A1/fr
Application granted granted Critical
Publication of EP1774179B1 publication Critical patent/EP1774179B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps
    • F04D29/164—Sealings between pressure and suction sides especially adapted for elastic fluid pumps of an axial flow wheel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/12—Blades
    • F01D5/14—Form or construction
    • F01D5/20—Specially-shaped blade tips to seal space between tips and stator
    • 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/321—Rotors specially for elastic fluids for axial flow pumps for axial flow compressors
    • F04D29/324—Blades
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49316—Impeller making
    • Y10T29/4932—Turbomachine making
    • Y10T29/49321—Assembling individual fluid flow interacting members, e.g., blades, vanes, buckets, on rotary support member
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49316—Impeller making
    • Y10T29/49336—Blade making

Definitions

  • the invention relates to a compressor blade for a compressor, which has a blade root, a platform region and an adjoining blade profile with a profile tip along a main axis, which blade profile is formed by a convex suction side wall and a concave pressure side wall lying opposite the suction side wall Walls, based on a Strömungs ⁇ medium, extending from a leading edge to a trailing edge and between which a profile center line runs centrally, wherein the profiled tip a transverse to the main axis end face is arranged on the at least one integrally formed with the blade profile sealing lip partly from the leading edge to the trailing edge, at a distance from the suction side wall and from the pressure side wall along the profile center line, and the blade profile, including the sealing lip, extends in the direction of the main axis height.
  • a turbine blade with a sealing lip molded onto the blade is known from US Pat. No. 6,039,531.
  • the sealing lip extends centrally between the suction side and the pressure side at the profile tip.
  • JP-A-2000130102 discloses a compressor blade which has an end face at its free end of the blade profile, on which a lip-like rib extends in the region of the suction side of the blade profile from an inflow edge to an outflow edge.
  • the rib of the compressor blade serves as a sealing element during operation of the compressor in order to reduce the peak gap losses in the compressor which occur between the blade tip and the boundary of the distributor channel.
  • the production of such a sealing rib on the suction side of the blade with a squeal edge can be cost-intensive, particularly in the case of edge zone-corrected blades, that are particularly strongly curved in the tip region, since the production or contour milling is performed by means of a five-axis milling cutter. After milling the suction side wall and the sealing lip geometry, the blade is ground manually on the suction side in order to achieve the required surface quality. This manual processing leads to frequent manufacturing errors with corresponding disadvantages, such as rejects or non-optimal contours.
  • the object of the invention is therefore to provide an aerodynamically improved compressor blade without reducing the sealing effect of the sealing lip. Moreover, it is an object of the invention to provide a cost-effective method for producing such a compressor blade and a use of these.
  • the invention proposes that the height of the sealing lip is less than two percent of the height of the blade profile.
  • the invention is based on the recognition that a sealing lip of a compressor blade according to the invention is produced inexpensively by a three-axis milling device, although due to the geometrically demanding, aerodynamic shape of the blade profile of the compressor blade this mit ⁇ means of a five-axis milling device or made by precision forging.
  • the accuracy of the geometry of the sealing lip according to the invention can be checked and controlled more easily than that of a sealing lip which is executed parallel to the suction side. This leads to a further reduction in production costs.
  • the height of the sealing lip is at most two percent of the height of the blade profile. Previously, a sealing lip integrally connected to the blade profile had a greater height for manufacturing reasons.
  • the sealing lip has a suction-side side surface and a pressure-side side surface which run parallel to the main axis, this can be particularly simple and thus produced inexpensively.
  • the sealing lip reduces the tip gap losses over the profile tip.
  • the side surfaces of the sealing lip are connected to one another by means of a rubbing surface, which rubbing surface is perpendicular to the radius of the rotor of the compressor.
  • a cylindrical gap can be formed between the housing or hub components and the compressor blade, which reduces the gap losses.
  • the compressor blade according to the invention can advantageously be used advantageously as a moving blade as well as a guide blade.
  • At least one side surface of the sealing lip is connected to the end face over a transition radius, whose size is at most 25 percent of the height of the sealing lip. Due to the particularly small transition radius, an extremely low sealing lip height can be achieved. The production of such a transition radius takes place cost-effectively together with the sealing lip by means of an end mill on a three-axis milling device.
  • strongly curved blade profiles with a sealing lip milled with a large transition radius have been found especially in the middle region between the leading edge and outflow edge on a larger sealing lip height than in the region of the inflow and Abström ⁇ edge, which previously led to flow disturbances. This kon ⁇ vexe course of the sealing lip or its height can be avoided with wesentlie ler smaller transition radii.
  • FIG. 1 shows a longitudinal partial section through a gas turbine with a compressor
  • FIG. 2 shows a compressor blade according to the invention in a perspective view
  • FIG. 1 shows a gas turbine 1 with a rotor 5 rotatably mounted about a rotation axis 3.
  • the gas turbine 1 has a suction hood 7, a compressor 9, a toroidal annular combustion chamber 11 and a turbine unit 13.
  • both in the compressor 9 and in the turbine unit 13 guide vanes 15 and blades 17 are each arranged in rings.
  • a rotor blade ring 19 follows a rotor blade ring 19.
  • the rotor blades 17 are fastened to the rotor 5 by means of rotor disks 23, whereas the stator blades 15 are fixedly mounted on the housing 25.
  • wreaths 21 are arranged from longitudinal blades 15, which, viewed in the direction of the flow medium, are followed by a ring of moving blades 17.
  • the respective blade profiles of the guide vanes 15 and of the rotor blades 17 extend radially in an annular flow channel 27.
  • air 29 is sucked through the intake manifold 7 and compressed by the compressor.
  • the compressed air is guided to the burners 33, which lie on a ring at the ring combustion chamber 11 are provided.
  • the compressed air 29 is mixed with a combustion agent 35, which mixture in the annular combustion chamber 11 is burned to a hot gas 37.
  • the hot gas 37 flows through the flow channel 27 of the turbine unit 13 past guide vanes 15 and blades 17.
  • the hot gas 37 relaxes on the rotor blades 17 of the turbine unit 13 in an efficient manner.
  • the rotor 5 of the gas turbine 1 is set in a rotational movement, which serves to drive the compressor 9 and to drive a work machine, not shown.
  • the compressor blade 50 has along a main axis 53 a blade root 55, a platform region 57 with a platform 59 and a blade profile 61.
  • the airfoil profile 61 flows around the airfoil profile 61, which connects the airfoil profile 61 to an inflow edge 63 and flows away from an outflow edge 65.
  • the blade profile 61 is formed by a pressure side wall 67 and by a suction side wall 69 and has a blade height H extending in the direction of the main axis 53.
  • a profile center line 71 which has at each point of its course a vertical, which perpendicular 74 both the suction side wall 69 and the pressure e'itenwand 67 intersects.
  • a first distance A between the points of intersection of the perpendicular 74 with the profile center line 71 and the pressure side wall 67 with the perpendicular 74 is identical to a second distance B which is between the intersections of the profile center line 71 with the vertical 74 and the suction side wall 69 with the vertical 74, is present.
  • the blade profile 61 on its profile tip 72 facing away from the platform 59 has an end face 73 on which a sealing lip 75 is arranged.
  • the sealing lip 75 is narrower than the blade profile 61, extends from strömkante 63 to the discharge edge 65 and extends along the Profilmittenllnie 71, ie at a distance between the contour of the suction side wall 69 and the pressure side wall 67th
  • the sealing lip 75 also called the squealer edge, has a first side surface 77 facing the pressure side wall 67 and a second side surface 79 facing the suction side wall 69.
  • the curved side surfaces 77, 79 of the sealing lip 75 extend parallel to the main axis 53 and also parallel to the profile center line 71, whereas the suction side wall 69 of the blade profile 61 and the pressure side wall 67 of the blade profile 61 are inclined for aerodynamic reasons, i. obliquely, to the main axis 53 run. Compared with a blade of the prior art, a simplified production of the sealing lip 75 can thereby be achieved.
  • the side surfaces 77, 79 of the sealing lip 75 mit ⁇ means of a Anstreifflache 81, connected to each other, which abraded surface 81 is perpendicular to the radius of the rotor 5 of the compressor 9.
  • the sealing lip 75 has a height HL directed parallel to the main axis 53, which height is measured between the end face 73 of the blade profile and the abutting surface 81 and is part of the blade profile height H.
  • FIG. 3 shows a detailed view of an An ⁇ grazing edge according to the invention. It can be clearly seen here that the sealing lip 75 extends centrally between the suction side wall 69 and the pressure side wall 67 from the leading edge 63 to the trailing edge 65, with side surfaces 77, 79 aligned parallel to the main axis 53 and the profile line 71.
  • the side surfaces 77, 79 pass over a transition radius R in the end face 73, which is advantageously at most 25 percent of the sealing lip height HL.
  • a particularly low sealing lip can be produced, whose height HL carries a maximum of 2 percent of the blade height H be ⁇ .
  • the new geometry and position of the sealing lip 75 eliminates error-prone and cost-intensive production steps. As a result, both the manufacturing costs and the reject rate of the manufactured compressor blades 50 can be reduced. A deterioration of the top gap losses across the radial gap between the compressor blade 50 and the inner housing does not occur, as well as flow losses due to the insignificantly reduced, maximum possible aerodynamically effective profile surface.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP05767976A 2004-08-06 2005-06-20 Aube de compresseur Active EP1774179B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP05767976A EP1774179B1 (fr) 2004-08-06 2005-06-20 Aube de compresseur
PL05767976T PL1774179T3 (pl) 2004-08-06 2005-06-20 Łopatka sprężarki

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP04018728A EP1624192A1 (fr) 2004-08-06 2004-08-06 Aube de rouet pour compresseur axial
PCT/EP2005/052848 WO2006015899A1 (fr) 2004-08-06 2005-06-20 Aube de compresseur et fabrication et utilisation d'une aube de compresseur
EP05767976A EP1774179B1 (fr) 2004-08-06 2005-06-20 Aube de compresseur

Publications (2)

Publication Number Publication Date
EP1774179A1 true EP1774179A1 (fr) 2007-04-18
EP1774179B1 EP1774179B1 (fr) 2011-08-03

Family

ID=34926091

Family Applications (2)

Application Number Title Priority Date Filing Date
EP04018728A Withdrawn EP1624192A1 (fr) 2004-08-06 2004-08-06 Aube de rouet pour compresseur axial
EP05767976A Active EP1774179B1 (fr) 2004-08-06 2005-06-20 Aube de compresseur

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP04018728A Withdrawn EP1624192A1 (fr) 2004-08-06 2004-08-06 Aube de rouet pour compresseur axial

Country Status (11)

Country Link
US (1) US8951008B2 (fr)
EP (2) EP1624192A1 (fr)
JP (1) JP4660547B2 (fr)
CN (1) CN100523519C (fr)
AT (1) ATE519036T1 (fr)
CA (1) CA2575948C (fr)
ES (1) ES2370402T3 (fr)
MX (1) MX2007001443A (fr)
PL (1) PL1774179T3 (fr)
RU (1) RU2343322C2 (fr)
WO (1) WO2006015899A1 (fr)

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GB0807358D0 (en) * 2008-04-23 2008-05-28 Rolls Royce Plc Fan blade
DE102010034604A1 (de) * 2010-08-13 2012-02-16 Ziehl-Abegg Ag Flügelrad für einen Ventilator
CN102536897B (zh) * 2010-12-29 2015-04-22 台达电子工业股份有限公司 风扇及其叶轮
FR2972380A1 (fr) 2011-03-11 2012-09-14 Alstom Technology Ltd Procede de fabrication d'un diaphragme de turbine a vapeur
US8790088B2 (en) * 2011-04-20 2014-07-29 General Electric Company Compressor having blade tip features
RU2476729C1 (ru) * 2011-07-29 2013-02-27 Открытое акционерное общество "Научно-производственное объединение "Сатурн" (ОАО "НПО "Сатурн") Рабочее колесо осевого компрессора газотурбинного двигателя
EP2798175A4 (fr) * 2011-12-29 2017-08-02 Rolls-Royce North American Technologies, Inc. Moteur à turbine à gaz et aube de turbine
JP5555727B2 (ja) 2012-01-23 2014-07-23 川崎重工業株式会社 軸流圧縮機翼の製造方法
EP2696031B1 (fr) 2012-08-09 2015-10-14 MTU Aero Engines AG Aube pour une turbomachine et turbomachine correspondante
CN103883361B (zh) * 2012-12-20 2016-05-04 中航商用航空发动机有限责任公司 涡轮叶片
CN103925244B (zh) * 2014-04-02 2017-03-15 清华大学 一种用于300mw f级重型燃气轮机的大流量高负荷轴流压气机
US20160238021A1 (en) * 2015-02-16 2016-08-18 United Technologies Corporation Compressor Airfoil
US10934847B2 (en) * 2016-04-14 2021-03-02 Mitsubishi Power, Ltd. Steam turbine rotor blade, steam turbine, and method for manufacturing steam turbine rotor blade
CN106271469B (zh) * 2016-08-29 2018-03-30 中航动力股份有限公司 一种细长空心多腔薄壁压气机叶片的加工方法
CN111219362A (zh) * 2018-11-27 2020-06-02 中国航发商用航空发动机有限责任公司 轴流压气机叶片、轴流压气机及燃气轮机
CN110076524B (zh) * 2019-04-30 2020-07-31 沈阳透平机械股份有限公司 一种轴流型压缩机静叶流道板的加工方法
DE102021130682A1 (de) 2021-11-23 2023-05-25 MTU Aero Engines AG Schaufelblatt für eine Strömungsmaschine

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Also Published As

Publication number Publication date
CA2575948C (fr) 2010-10-19
JP4660547B2 (ja) 2011-03-30
CA2575948A1 (fr) 2006-02-16
WO2006015899A1 (fr) 2006-02-16
EP1624192A1 (fr) 2006-02-08
MX2007001443A (es) 2007-04-19
EP1774179B1 (fr) 2011-08-03
CN101035988A (zh) 2007-09-12
US8951008B2 (en) 2015-02-10
RU2343322C2 (ru) 2009-01-10
CN100523519C (zh) 2009-08-05
ATE519036T1 (de) 2011-08-15
US20110044800A1 (en) 2011-02-24
PL1774179T3 (pl) 2011-12-30
JP2008509316A (ja) 2008-03-27
RU2007108295A (ru) 2008-09-20
ES2370402T3 (es) 2011-12-15

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