EP3158204A1 - Rotor de compresseur radial et compresseur radial associé - Google Patents

Rotor de compresseur radial et compresseur radial associé

Info

Publication number
EP3158204A1
EP3158204A1 EP15763593.9A EP15763593A EP3158204A1 EP 3158204 A1 EP3158204 A1 EP 3158204A1 EP 15763593 A EP15763593 A EP 15763593A EP 3158204 A1 EP3158204 A1 EP 3158204A1
Authority
EP
European Patent Office
Prior art keywords
compressor impeller
radial compressor
blades
wheel disc
rounded edge
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Withdrawn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
EP15763593.9A
Other languages
German (de)
English (en)
Inventor
Werner Jonen
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
Publication of EP3158204A1 publication Critical patent/EP3158204A1/fr
Withdrawn legal-status Critical Current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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/30—Vanes
    • 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
    • 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
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
    • 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
    • F05D2240/00—Components
    • F05D2240/20—Rotors
    • F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
    • F05D2240/304—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor related to the trailing edge of a rotor blade

Definitions

  • the invention relates to a radial compressor impeller with a wheel disc, a cover disk spaced therefrom and arranged therebetween, the wheel disk and the cover disk ver ⁇ binding blades.
  • wheels are used for example in compressors or fans.
  • the wheel disc of such a radial compressor impeller has blades, the z. B. are milled from the solid, then a cover disk is fastened ⁇ tigt on the blades, whereby the radial compressor impeller is formed.
  • a conventional centrifugal compressor impeller is arranged on a ⁇ be driven shaft.
  • the radial compressor impeller is surrounded by a housing, by rotation of the
  • Radial compressor rotor a gas which flows axially into the interim ⁇ rule space between wheel disc and the cover disc, ra ⁇ dial and accelerated in the circumferential direction and be compressed thereby.
  • the flowing gas passes after passing through the radial compressor impeller in a channel of the housing.
  • Radial compressor impeller is coupled by interaction with the wheel sidewall flow. This interaction influences the performance, in particular the achievable printer ⁇ increase and the efficiency of a compressor stage.
  • pressure losses occur in the trailing edge and there are displacement and constriction effects in the impeller outlet flow due to the inflow of gas from the impeller sidewall into the impeller flow. This will increase the pressure of the
  • Radial compressor impeller of the type mentioned inventions ⁇ tion provided according to that the blades have one of the radially outer end of the wheel disc and the cover plate in ⁇ nen spaced end portion with a reduced thickness relative to an adjoining portion.
  • the blades of the radial compressor impeller according to the invention are "shortened", ie formed shortened and they do not extend radially to the outer end of wheel disc and cover disc but they have a radially offset or from the outer end inwardly disposed end portion.
  • the radially outer end portions of the blades a redu ⁇ ed thickness, based on the thickness of the adjacent from ⁇ -section of the blades.
  • the reduced thickness is preferably only provided in front of finely ⁇ in the area of the end portion of the Schau-, whereas the blades in the subsequent section do not have reduced thickness.
  • Compressor be influenced at a specified speed in the desired manner.
  • mixing losses at the impeller outlet, whereby the devisnwir ⁇ ciency is increased decrease.
  • the "cut" of the blades, that is their reduced diameter may be 1% to 15%, based on the “unabridged” diameter d of the wheel and / or cover plate.
  • a further development of the invention provides that the end portions of the vanes each having a saucerun ⁇ an end edge on the suction side. It was recognized that a thick
  • Vane trailing edge causes significant pressure losses with correspondingly pronounced trailing dents in the
  • Impeller flow in addition, there is a mixture of the
  • the rounded edge and the profile of the blade on the suction side preferably merge into one another continuously.
  • Wheel disc - and a is a factor between 0.1 and 0.3, which is preferably 0.2.
  • the rounded edge does not extend over the entire width of the radial outer end of the blades, but only over about two-thirds of the width.
  • the radial outer end of the blades is parallel to the outer periphery of Wheel disc and the cover plate formed, alternatively, it may also be formed as a tangent.
  • the end sections of the blades each have a rounded edge on the pressure side. Analogously or vice versa to the rounded edge on the suction side thus has the pressure side on a rounded edge. Accordingly, the aerodynamic properties of the self ⁇ centrifugal compressor impeller according to the invention can in a targeted manner by modifying the profile of the suction side
  • the rounded edge may have a radius R, R ⁇ at least nä ⁇ herungrios the equation corresponds to b-d, where d is the diameter of the cover disc or the wheel disc and b is a factor between 0.1 and 0.3 which preferably carries 0.2 be ⁇ .
  • a variant of the radial compressor impeller according to the invention provides that approximately one third of the width of the ra ⁇ dialen outer end of the blades is approximately parallel to the outer periphery of the wheel disc and the cover disk is formed and that the rounded edge adjoins thereto.
  • the invention relates to a centrifugal compressor having a radial compressor impeller of the type described, which is accommodated in a housing.
  • FIG. 1 is a sectional view of a detail of a he ⁇ inventive radial compressor impeller.
  • FIG. 2 shows a section through the blade shown in FIG. 1 along the line II - II;
  • FIG. 1 is a sectional view of a detail of a he ⁇ inventive radial compressor impeller.
  • FIG. 2 shows a section through the blade shown in FIG. 1 along the line II - II;
  • FIG. 1 is a sectional view of a detail of a he ⁇ inventive radial compressor impeller.
  • FIG. 2 shows a section through the blade shown in FIG. 1 along the line II - II;
  • Fig. 3 is a similar sectional view as in FIG.
  • FIG. 4 shows a detail of FIG. 3 in the region of the end section of the blade
  • FIG. 5 is a similar sectional view of a show ⁇ fel as in Figure 2 according to another embodiment ⁇ example.
  • Fig. 6 shows a detail of the blade shown in Fig. 5 in the region of the end portion of the blade.
  • FIG. 1 shows a part of a radial compressor impeller 1 comprising a wheel disc 2 mounted on a shaft (not shown).
  • the radial compressor impeller 1 comprises a distance from the wheel disc 2 cover disk 3.
  • the space between the wheel ⁇ disc 2 and cover plate 3 are distributed circumferentially disposed blades 4 are arranged.
  • Radial compressor impeller 1 is surrounded on the outside by a housing 5, which is only partially shown in Fig. 1.
  • a gas flowing axially in the direction indicated by an arrow 6 can be accelerated radially and circumferentially and thereby compressed.
  • the gas passes through the radial compressor impeller 1 and flows into a flow channel 7 formed in the housing 5.
  • Fig. 2 is a sectional view of the
  • the blade 4 has an aerodynamic profile and a suction side includes a pressure side 8 and 9, the blade 4 has a nä ⁇ herungmac constant thickness over its length.
  • the blade 4 has an end portion 10 which is spaced from the radially outer end 11 of the wheel disc 2 and the cover disc 3 arranged approximately parallel thereto inwardly. Accordingly, the blade 4 is shortened at its radially outer end as compared with a conventional blade.
  • a radial compressor impeller for example, after performing a sketchStandtests, be modified by turning so that it reaches a predetermined increase in pressure , As part of the production of a new
  • the end portion of the blade can of course also be formed directly as shown in Fig. 2, ie with a spaced from the outer end of the wheel disc end portion.
  • FIGS. 3 and 4 show a further embodiment of a radial compressor impeller, wherein only - as in FIG. 2 - a section through a blade and in FIG. 4 a detail of the view of FIG. 3 is shown.
  • the blade 12 shown in Fig. 3 basically corresponds to the blade 4 shown in Fig. 2.
  • the blade 12 has an end portion 13 which is spaced from the radially outer end of the wheel disc 2 inwardly.
  • the end portion 13 of the blade 12 on the suction ⁇ page 8 a rounded edge 14.
  • the rounded edge 14 and the profile of the blade 12 on the suction side 8 merge into one another continuously, at this point the tangent condition is fulfilled, ie the edge 14 and the edge of the profile of the blade 12 have the same tangent at the point of contact.
  • the rounded edge 14 is a circle segment with a radius R us, which corresponds approximately to 0.2 times the diameter d of the wheel disc 2.
  • FIG. 4 it can be seen that approximately one third of the (not rounded) width of the radially outer end section 13 of the blade 12 is approximately parallel to the outer circumference of the wheel disc 2 and that the rounded edge 14 adjoins it.
  • the outer edge of the end portion 13 and the rounded edge 14 enclose an angle slightly greater than 90 °.
  • the rounded edge 14 having end portion 13 can be ⁇ 12 forms either directly in the preparation of blade 12 or integrally formed with the blades wheel disc, alternatively, the end portion 13 and subsequently by overtightening of a conventional blade is manufactured be.
  • the preparation of the rounded edge 14 may thus be regarded as "rounding up", that is normally present at this point edge is provided with a Ra ⁇ dius. Figs.
  • FIG. 5 and 6 show another embodiment ei ⁇ nes radial compressor impeller in the region of a blade, wherein Fig. 5 is a view similar to Figs. 2 and 3 and Fig. 6 is an enlarged detail of the blade shown in Fig. 5.
  • the blade 15 shown in FIGS. 5 and 6 has, in accordance with the exemplary embodiment shown in FIG. 2, an end section 16 which extends from the radial outer end 11 of the wheel disc 2 is spaced.
  • the end portion 16 of the "shortened" blade 15 has on the pressure side 9 a to ⁇ rounded edge 17. As best seen in Fig. 6 is to go see the rounded edge 17 and the outer contour of the Schau- fei 15 on the pressure side 9 The tangent condition is met at the point of contact.
  • the rounded edge 17 is formed as a circle segment whose radius corresponds to about 0.2 times the diameter d of the wheel disc 2. In other embodiments, a different radius can be provided, this can, for example, between 0.15 d and 0.25 d betra ⁇ gene. About one third of the width of the radial end portion 16 of the blade 15 is formed parallel to the outer periphery of the wheel disc 2, this is followed by the rounded edge 17, which thus extends approximately over two-thirds of the (gedach ⁇ th) width.
  • a conventional radial compressor impeller can be machined by Ausdre ⁇ hen of the radial end portion of the blades and by rounding on the pressure side, that results in the Radialverêtrlaufrad shown in Figs. 5 and 6.
  • Radial compressor impeller are formed directly by milling or other manufacturing process.
  • the different methods of influencing the flow conditions shown in the embodiments cause pressure losses are reduced and that a uner ⁇ desired mixing of fluid in the impeller side is reduced with fluid in the region of the impeller passage or avoided. In this way, the efficiency of the impeller stage increases.
  • the measures shown in the various embodiments described can also be combined with each other.
  • To provide a centrifugal compressor impeller with The modifications made in the area of the end sections of the blades can also be modified. For example, a rounded edge may be provided both on the suction side and on the pressure side. In addition, the remaining length of the blades in the radial direction or the distance from the outer edge of the wheel disc can be adjusted.

Landscapes

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

Abstract

L'invention concerne un rotor de compresseur radial (1) qui comporte un disque de roue (2), un disque de recouvrement (3) placé à distance de celui-ci et des aubes (4, 12, 15) qui sont disposées entre les disques, qui relient le disque de roue (2) et le disque de recouvrement (3) et qui comportent une partie d'extrémité (10, 13, 16) qui s'étend de l'extrémité radialement extérieure du disque de roue (2) et du disque de recouvrement (3) vers l'intérieur et qui a une épaisseur réduite par rapport à une partie adjacente.
EP15763593.9A 2014-09-22 2015-09-16 Rotor de compresseur radial et compresseur radial associé Withdrawn EP3158204A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014219058.4A DE102014219058A1 (de) 2014-09-22 2014-09-22 Radialverdichterlaufrad und zugehöriger Radialverdichter
PCT/EP2015/071174 WO2016046036A1 (fr) 2014-09-22 2015-09-16 Rotor de compresseur radial et compresseur radial associé

Publications (1)

Publication Number Publication Date
EP3158204A1 true EP3158204A1 (fr) 2017-04-26

Family

ID=54140466

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15763593.9A Withdrawn EP3158204A1 (fr) 2014-09-22 2015-09-16 Rotor de compresseur radial et compresseur radial associé

Country Status (6)

Country Link
US (1) US20170284412A1 (fr)
EP (1) EP3158204A1 (fr)
CN (1) CN106715920A (fr)
DE (1) DE102014219058A1 (fr)
RU (1) RU2017113691A (fr)
WO (1) WO2016046036A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016215738A1 (de) * 2016-08-23 2018-03-01 Siemens Aktiengesellschaft Laufrad, Verfahren zur Fertigung
EP3760875B1 (fr) * 2018-06-22 2022-06-15 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Rotor et machine à compression centrifuge équipée dudit rotor
CN214424762U (zh) * 2020-12-28 2021-10-19 罗伯特·博世有限公司 用于空气压缩机的叶轮及空气压缩机
DE102021119121A1 (de) 2021-07-23 2023-01-26 Ebm-Papst Mulfingen Gmbh & Co. Kg Radial- oder Diagonallaufrad mit modifizierter Schaufelkante

Family Cites Families (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3068801A (en) * 1958-09-02 1962-12-18 Murray William Centrifugal impeller pumps
US3145915A (en) * 1959-11-20 1964-08-25 Motcurs D Aviat Soc Nat D Etud Compressors for fluids
JPS6020598B2 (ja) * 1977-05-06 1985-05-22 トヨタ自動車株式会社 ガスタ−ビン用遠心圧縮機
SU688712A1 (ru) * 1978-04-26 1979-09-30 Всесоюзный научно-исследовательский институт природных газов Рабочее колесо центробежного компрессора
US4243357A (en) * 1979-08-06 1981-01-06 Cummins Engine Company, Inc. Turbomachine
DE3275000D1 (en) * 1981-08-07 1987-02-12 Holset Engineering Co Impeller for centrifugal compressor
JPH04123881A (ja) * 1990-09-11 1992-04-23 Hitachi Ltd 羽根車およびその電子ビーム溶接方法
US6261051B1 (en) * 1998-09-02 2001-07-17 Gordon A. Kolacny Fan duct combination unit
JP2003090298A (ja) * 2001-09-17 2003-03-28 Nippon Soken Inc 遠心ファン
CN100497951C (zh) * 2004-05-28 2009-06-10 株式会社日立金属精密 用于增压器的叶轮及其制造方法
EP1788255A1 (fr) * 2005-11-16 2007-05-23 Siemens Aktiengesellschaft Roue de compresseur radial
JP2010180721A (ja) * 2009-02-03 2010-08-19 Mitsubishi Heavy Ind Ltd インペラの製造方法および圧縮機
IT1394295B1 (it) * 2009-05-08 2012-06-06 Nuovo Pignone Spa Girante centrifuga del tipo chiuso per turbomacchine, componente per tale girante, turbomacchina provvista di tale girante e metodo di realizzazione di tale girante
JP5473457B2 (ja) * 2009-07-29 2014-04-16 三菱重工業株式会社 遠心圧縮機のインペラ
DE102011013677B4 (de) * 2011-03-11 2016-08-18 Ziehl-Abegg Se Lüfterrad
DE102011013841B4 (de) * 2011-03-14 2021-11-11 Nicotra Gebhardt GmbH Radialventilatorrad und Radialventilator
IN2014DN09484A (fr) * 2012-04-23 2015-07-17 Borgwarner Inc
CN102797703B (zh) * 2012-09-10 2015-04-15 三一能源重工有限公司 一种压缩机叶轮
US9541098B2 (en) * 2013-06-28 2017-01-10 Vyaire Medical Capital Llc Low-noise blower
CN103423168B (zh) * 2013-07-24 2015-10-14 大连理工大学 一种ap1000滤网反冲洗泵的水力模型
CN203430850U (zh) * 2013-07-30 2014-02-12 嘉善金亿精密铸件有限公司 一种叶轮

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
None *
See also references of WO2016046036A1 *

Also Published As

Publication number Publication date
CN106715920A (zh) 2017-05-24
RU2017113691A3 (fr) 2018-10-24
US20170284412A1 (en) 2017-10-05
DE102014219058A1 (de) 2016-03-24
RU2017113691A (ru) 2018-10-24
WO2016046036A1 (fr) 2016-03-31

Similar Documents

Publication Publication Date Title
EP2096316B1 (fr) Structuration de boîtier pour compresseur axial dans la zone du moyeu
EP1948939B1 (fr) Roue mobile de compresseur radial
EP1632662B1 (fr) Turbomachine avec soutirage
EP3408503B1 (fr) Turbomachine avec diffuseur à aubes
EP2696029B1 (fr) Grille d'aube avec définition de contour de la paroi latérale et turbomachine
DE102007056953B4 (de) Strömungsarbeitsmaschine mit Ringkanalwandausnehmung
EP2725194A1 (fr) Aube de rotor d'une turbine à gaz
EP1774179A1 (fr) Aube de compresseur et fabrication et utilisation d'une aube de compresseur
DE2551614A1 (de) Axial kurzer axialventilator
EP3158204A1 (fr) Rotor de compresseur radial et compresseur radial associé
EP2746534B1 (fr) Étage statorique et/ou rotorique de turbomachine, et turbine à gaz associée
EP3655665A2 (fr) Carter pour une turbomachine, notamment pour un ventilateur radial
DE102018128792A1 (de) Kompakter Diagonalventilator mit Nachleiteinrichtung
EP3256732B1 (fr) Roue pour un ventilateur et ventilateur
WO2016110373A1 (fr) Soufflante à canal latéral pour un moteur à combustion interne
DE102016102732A1 (de) Mixed-Flow-Turbinenrad eines Abgasturboladers sowie Abgasturbine mit einem solchen Turbinenrad
EP2827003B1 (fr) Grille de guidage de compresseur à turbines à gaz
EP2410131A2 (fr) Rotor d'une turbomachine
DE102014203604A1 (de) Schaufelreihengruppe
EP3273066B1 (fr) Roue de ventilateur
WO2016046112A1 (fr) Rotor de compresseur centrifuge radial et compresseur centrifuge radial associé
DE202015100654U1 (de) Ventilatorrad und Ventilator
WO2019115703A1 (fr) Roue de ventilateur diagonal a resistance amelioree
EP3592985A1 (fr) Ensemble de pièces et procédé de fabrication d'un ventilateur radial
EP3203084B1 (fr) Roue de ventilateur et systeme de ventilateur

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20170119

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: SIEMENS AKTIENGESELLSCHAFT

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20190912

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20200123