EP2209995A1 - Rotor de pompe à plusieurs étages pour pompes turbomoléculaires - Google Patents

Rotor de pompe à plusieurs étages pour pompes turbomoléculaires

Info

Publication number
EP2209995A1
EP2209995A1 EP08804453A EP08804453A EP2209995A1 EP 2209995 A1 EP2209995 A1 EP 2209995A1 EP 08804453 A EP08804453 A EP 08804453A EP 08804453 A EP08804453 A EP 08804453A EP 2209995 A1 EP2209995 A1 EP 2209995A1
Authority
EP
European Patent Office
Prior art keywords
rotor
rings
pump
pump rotor
turbomolecular pump
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
EP08804453A
Other languages
German (de)
English (en)
Other versions
EP2209995B1 (fr
Inventor
Heinrich Engländer
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.)
Leybold GmbH
Original Assignee
Oerlikon Leybold Vacuum GmbH
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=40184986&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP2209995(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Oerlikon Leybold Vacuum GmbH filed Critical Oerlikon Leybold Vacuum GmbH
Publication of EP2209995A1 publication Critical patent/EP2209995A1/fr
Application granted granted Critical
Publication of EP2209995B1 publication Critical patent/EP2209995B1/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
    • F04D19/00—Axial-flow pumps
    • F04D19/02—Multi-stage pumps
    • F04D19/04—Multi-stage pumps specially adapted to the production of a high vacuum, e.g. molecular pumps
    • F04D19/042—Turbomolecular vacuum 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
    • F04D19/00—Axial-flow pumps
    • F04D19/02—Multi-stage pumps
    • F04D19/04—Multi-stage pumps specially adapted to the production of a high vacuum, e.g. molecular pumps
    • F04D19/048—Multi-stage pumps specially adapted to the production of a high vacuum, e.g. molecular pumps comprising magnetic bearings
    • 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
    • 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
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/64—Mounting; Assembling; Disassembling of axial pumps
    • F04D29/644—Mounting; Assembling; Disassembling of axial pumps especially adapted for elastic fluid pumps

Definitions

  • the invention relates to a multi-stage pump rotor of a turbomolecular pump.
  • Prior art turbomolecular pumps operate at speeds of several tens of thousands of revolutions per minute.
  • the kinetic energy of a pump rotor operated at such a nominal speed is, in the case of larger turbomolecular pumps, within the range of the kinetic energy of a small car at a speed of 50-70 km / h.
  • this high kinetic energy of the rotor constitutes a high potential for destruction and injury, which can only be controlled with great effort for the mechanical shielding of the rotor.
  • turbomolecular pump pump rotors which are magnetically supported.
  • it is endeavored to arrange at least one radial bearing and the drive motor in the region of the center of gravity of the pump rotor.
  • the pump rotor is bell-shaped to accommodate the Nagnetlagerung and possibly also the drive motor in the bell cavity within the pump rotor.
  • the bell-shaped construction of the pump rotor results in a design-related mechanical weakening of the rotor.
  • the usually one-piece turbomolecular pump pump rotors can be countered only by the use of high-strength aluminum alloys, which are extremely expensive because of this design-induced weakening.
  • the object of the invention is to provide a multi-stage turbomolecular pump pump rotor having improved strength.
  • the pump rotor according to the invention is no longer in one piece and has at least two separate wing disk rings, each having a rotor ring and at least one wing disk.
  • the ends of the two rotor rings of adjacent wing disc rings are on the outside without play by a cylindrical Arm michsrohr, which is arranged between the adjacent wing discs of the adjacent rotor discs rings.
  • the reinforcing tube is not necessarily the axial and radial fixation of the two rotor rings to each other, but it includes the two rotor rings so tightly that it receives at least a portion of the centrifugal forces in the rotor ring resulting tangential forces and mechanically relieved the rotor rings in this way.
  • the pump rotor is no longer one piece, but designed in several pieces.
  • the pump rotor can be formed from a plurality of rotor rings, each with a single wing disc. Even if a rotor ring by high Centrifugal forces should break tangentially, this fraction remains locally limited to the respective rotor ring and can not readily extend to the entire pump rotor.
  • the respective components are specialized for their function. This makes it possible to optimize both the rotor ring and the reinforcing tube in terms of their function, namely the holding of the rotor blades on the one hand and the inclusion of the tangential forces on the other.
  • the rotor ring may for example consist of inexpensive and average tensile aluminum alloys or other materials.
  • a material is selected that can absorb high tensile forces.
  • the wing disk or the rotor blades can be made easier, or take more complex forms. This can lead to an improvement in the fluid mechanics in the pump stages at higher pressures within the turbomolecular pump receiving the pump rotor.
  • the total weight of the pump rotor can be reduced.
  • the wing disc ring can each, but need not, be integrally formed.
  • the wing disc ring may alternatively be composed of several segments. In the division of the rotor ring into several segments occur in the rotor ring virtually no tangential forces and these are introduced exclusively in the reinforcing tube.
  • the Fiügelinring is formed but eän harmonyig.
  • the closed one-piece wing disc ring is easier to produce and assemble.
  • the Arm istsrohr material is different from the material of the wing disc rings.
  • CFRP a material for the reinforcing tube CFRP
  • carbon fiber reinforced plastic is preferably used, which is particularly suitable because of its ability to absorb high tensile forces and because of its low weight as a material for the reinforcing tube.
  • At least one Rotorfiügelular on a single wing disk of rotor blades at least one Rotorfiügelular on a single wing disk of rotor blades.
  • the Limiting the rotor ring or rings to a single wing disc makes it possible to arrange a reinforcing tube between each wing wing pair of adjacent wing discs. As a result, a maximum of strength of the pump rotor with respect to the tangential forces is achieved.
  • not all of the impeller disk rings of the pump rotor necessarily have only a single disk disk.
  • wing disc rings are provided with a single wing disc, while in other axial areas of the pump rotor, where lower tagentiate forces occur or in which the rotor ring can be built radially stronger in that the wing disc ring concerned may also have two or more wing discs.
  • the wing disc rings are clamped axially axially between two rotor shaft clamping bodies.
  • the rotor rings may, for example, be self-centering with corresponding axial annular grooves and annular lands and be clamped together axially by the two rotor shaft clamping bodies.
  • at least one rotor support body may be provided, onto which the rotor rings of the wing disk rings are pushed.
  • the rotor support body may form the clamping body, but the clamping body but may also be formed separately from the rotor bearing bearing rotor support kör pern.
  • the rotor support body may be made of a different material than the rotor rings or the reinforcing tubes.
  • the pump rotor has a cavity for receiving a rotor bearing, which is preferably a magnetic bearing.
  • a rotor bearing which is preferably a magnetic bearing.
  • the axial denomination of the pump rotor in individual rotor rings is particularly advantageous because in particular the cavity portion of the pump rotor is exposed due to the limitation of the pump rotor space high tangential loads.
  • Fig. 1 shows a first Principalsbe ⁇ spiel a multi-stage
  • FIGS. 1 and 2 each show a multi-stage turbomolecule pump pump rotor 10; 40 shown.
  • the pump rotor 10; 40 can rotate at rated speeds between 20,000 and 100,000 rpm.
  • the two pump rotors 10; 40 are essentially the same structure and differ only in their internal structure.
  • the pump rotor 10 of Figure 1 is essentially formed by eight wing disc rings 17 which are axially braced together by two by a clamping screw 28 and a WeMe 30 axially braced clamping body 20, 22. Furthermore, the wing disc rings 17 is followed by a rotor-side Holweck cylinder 32.
  • the pump rotor 10 is not formed in one piece, as is usual in pump rotors according to the prior art, but is composed of a plurality of flywheel rings 17.
  • Each wing disc ring 17 is formed by a closed rotor ring 12, protrude from the radially rotor blades 16 to the outside, which in turn form a wing disc 14.
  • the rotor rings 12 are axially held together by the two axial clamping body 20, 22, which are braced axially by the clamping screw 28 and the shaft 30 together.
  • the two clamping bodies 20, 22 each also have outer cylindrical rotor support bodies 24, 26, on the support cylinders 25, 27, 29, 31 of which the respective rotor rings 12 are attached.
  • the rotor support bodies 24, 26 are used for the radial positioning or fixing of the rotor rings 12.
  • the outlet-integral piece clamping body 22 is formed in three stages, and has three support cylinders 27,29,31 on.
  • the rotor rings 12 sit with a slight clamping fit without gaps on the rotor support bodies 24, 26 and their support cylinders 25, 27, 29, 31.
  • the clamping screw 28 braces the rotor shaft 30, the pressure-side rotor support body 26 and the inlet-side rotor support body 24 axially together.
  • Each rotor ring 12 has an axial shoulder 15 at one or both axial ends.
  • a reinforcing tube 18 made of glass fiber reinforced plastic (CFRP) is placed axially under prestress.
  • the Arm michsrohre 18 take on rotation of the pump rotor 10 substantially on the generated by the centrifugal force in the rotor ring 12 tangential forces. In this way, 17 can be used as a material for the integral wing disk rings relatively inexpensive aluminum alloys.
  • the pressure-side rotor support body 26 has on the inside a hollow space 38, which has sufficient space for the arrangement of a rotor bearing of the rotor shaft 30, wherein the rotor bearing is preferably a magnetic bearing.
  • a Holweck cylinder 32 can connect to the pressure-side end of the pressure-side rotor support body 26.
  • the pump rotor 40 of Figure 2 has compared to the pump rotor 10 of Figure 1 only a modified structure of the rotor support body and clamping body.
  • a total of three rotor support bodies 24, 42, 48 are provided.
  • the einiass workede rotor support body 24 forms with the central rotor support body 42 two clamping bodies 20, 43, through which the three inlet side FSügeiusionnringe 17 are clamped together axially.
  • the remaining wing disc rings 17 ' are not axially braced, but axially fixed to each other by other design measures.
  • the central rotor support body 42 and the pressure-side rotor support body 48 are each formed in two pieces and each consist of a disk body 44, 52 and a cylindrical support cylinder 46, 50.
  • the disk body 44, 52 is made of aluminum and the support cylinder 46, 50 of carbon fiber reinforced plastic.
  • the two-component structure of the two rotor support bodies 42, 48 allows a further mass reduction of the rotor 40, whereby the kinetic rotation energy is reduced, which in turn has the consequence that the energy released in a rotor burst is lower, and realized higher speeds because of the reduced centrifugal forces can be.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Non-Positive Displacement Air Blowers (AREA)

Abstract

L'invention concerne un rotor de pompe (10) à plusieurs étages pour une pompe turbomoléculaire. Le rotor de pompe (10) présente au moins deux couronnes à palettes (17) séparées, comprenant chacune un anneau de rotor (12) et au moins un disque à palettes (14). Un tube de renforcement cylindrique (18) est prévu entre les disques à palettes voisins (14) de couronnes à palettes voisines (17) ; il entoure extérieurement sans jeu les anneaux de rotor (12) des couronnes à palettes (17). Le tube de renforcement (18) absorbe une grande partie des forces tangentielles rencontrées en fonctionnement, de sorte que le rotor de pompe (10) présente une résistance mécanique améliorée à des vitesses de rotation élevées.
EP08804453A 2007-10-11 2008-09-19 Rotor de pompe à plusieurs étages pour pompes turbomoléculaires Active EP2209995B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007048703A DE102007048703A1 (de) 2007-10-11 2007-10-11 Mehrstufiger Turbomolekularpumpen-Pumpenrotor
PCT/EP2008/062519 WO2009049988A1 (fr) 2007-10-11 2008-09-19 Rotor de pompe à plusieurs étages pour pompes turbomoléculaires

Publications (2)

Publication Number Publication Date
EP2209995A1 true EP2209995A1 (fr) 2010-07-28
EP2209995B1 EP2209995B1 (fr) 2012-11-14

Family

ID=40184986

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08804453A Active EP2209995B1 (fr) 2007-10-11 2008-09-19 Rotor de pompe à plusieurs étages pour pompes turbomoléculaires

Country Status (7)

Country Link
US (1) US8562293B2 (fr)
EP (1) EP2209995B1 (fr)
JP (1) JP5674468B2 (fr)
CN (1) CN101828040B (fr)
DE (1) DE102007048703A1 (fr)
TW (1) TWI453345B (fr)
WO (1) WO2009049988A1 (fr)

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2462804B (en) * 2008-08-04 2013-01-23 Edwards Ltd Vacuum pump
JP5412239B2 (ja) * 2009-02-24 2014-02-12 株式会社島津製作所 ターボ分子ポンプおよびターボ分子ポンプ用パーティクルトラップ
DE102009035812A1 (de) * 2009-08-01 2011-02-03 Pfeiffer Vacuum Gmbh Turbomolekularpumpenrotor
JP5704157B2 (ja) 2010-02-16 2015-04-22 株式会社島津製作所 真空ポンプ
EP2623791B1 (fr) * 2010-09-28 2019-12-04 Edwards Japan Limited Pompe d'évacuation
CN102011745B (zh) * 2010-12-31 2013-08-07 清华大学 一种磁悬浮分子泵的神经网络控制系统及方法
JP5664253B2 (ja) * 2011-01-12 2015-02-04 株式会社島津製作所 高真空ポンプ
US9314547B2 (en) 2011-09-09 2016-04-19 Abyrx Inc. Absorbable multi-putty bone cements and hemostatic compositions and methods of use
DE202013006436U1 (de) * 2013-07-17 2014-10-22 Oerlikon Leybold Vacuum Gmbh Rotorelement für eine Vakuumpumpe
US9827349B1 (en) 2013-11-26 2017-11-28 Abyrx Inc. Settable surgical implants and their packaging
DE202013010937U1 (de) 2013-11-30 2015-03-02 Oerlikon Leybold Vacuum Gmbh Rotorscheibe sowie Rotor für eine Vakuumpumpe
DE102014100622A1 (de) 2014-01-21 2015-07-23 Pfeiffer Vacuum Gmbh Verfahren zur Herstellung einer Rotoranordnung für eine Vakuumpumpe und Rotoranordnung für eine Vakuumpumpe
CN104929978B (zh) * 2015-06-17 2018-01-05 川北真空科技(北京)有限公司 一种新型抗冲击分子泵转子
EP3786457B1 (fr) * 2020-09-09 2022-09-07 Pfeiffer Vacuum Technology AG Système de rotor pour une pompe à vide, pompe à vide et procédé de fabrication d'une telle pompe à vide
GB2621837A (en) * 2022-08-23 2024-02-28 Leybold Gmbh Rotor assembly and vacuum pump

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US4312628A (en) * 1979-05-21 1982-01-26 Cambridge Thermionic Corporation Turbomolecular vacuum pump having virtually zero power magnetic bearing assembly with single axis servo control
JPS5993993A (ja) * 1982-11-22 1984-05-30 Hitachi Ltd タ−ボ分子ポンプ用ロ−タ
JPS60203375A (ja) * 1984-03-28 1985-10-14 Hitachi Ltd タ−ボ分子ポンプのロ−タの製作方法
JPS6138194A (ja) * 1984-07-30 1986-02-24 Hitachi Ltd 高速度回転ロ−タ
JPS6444498U (fr) * 1987-09-11 1989-03-16
JPH0759955B2 (ja) * 1988-07-15 1995-06-28 ダイキン工業株式会社 真空ポンプ
JP3160039B2 (ja) * 1991-08-22 2001-04-23 エヌティエヌ株式会社 ターボ分子ポンプと動翼の加工方法
DE10010371A1 (de) * 2000-03-02 2001-09-06 Pfeiffer Vacuum Gmbh Turbomolekularpumpe
DE10331932B4 (de) * 2003-07-15 2017-08-24 Pfeiffer Vacuum Gmbh Turbomolekularpumpe
DE10353034A1 (de) * 2003-11-13 2005-06-09 Leybold Vakuum Gmbh Mehrstufige Reibungsvakuumpumpe
JP2005180265A (ja) * 2003-12-18 2005-07-07 Boc Edwards Kk 真空ポンプ
JP2006046074A (ja) * 2004-07-30 2006-02-16 Boc Edwards Kk 真空ポンプ
DE102006020081A1 (de) * 2006-04-29 2007-10-31 Pfeiffer Vacuum Gmbh Rotor- oder Statorscheibe für eine Molekularpumpe
GB2462804B (en) 2008-08-04 2013-01-23 Edwards Ltd Vacuum pump

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Title
See references of WO2009049988A1 *

Also Published As

Publication number Publication date
WO2009049988A1 (fr) 2009-04-23
US20100290915A1 (en) 2010-11-18
JP2011501010A (ja) 2011-01-06
CN101828040B (zh) 2012-05-30
TW200925431A (en) 2009-06-16
DE102007048703A1 (de) 2009-04-16
EP2209995B1 (fr) 2012-11-14
CN101828040A (zh) 2010-09-08
TWI453345B (zh) 2014-09-21
US8562293B2 (en) 2013-10-22
JP5674468B2 (ja) 2015-02-25

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