US20120275923A1 - Rotor for a turbo-machine - Google Patents

Rotor for a turbo-machine Download PDF

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Publication number
US20120275923A1
US20120275923A1 US13/509,122 US201013509122A US2012275923A1 US 20120275923 A1 US20120275923 A1 US 20120275923A1 US 201013509122 A US201013509122 A US 201013509122A US 2012275923 A1 US2012275923 A1 US 2012275923A1
Authority
US
United States
Prior art keywords
shaft
bearing
rotor
recess
rotor wheel
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.)
Abandoned
Application number
US13/509,122
Other languages
English (en)
Inventor
Norbert Wagner
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
Assigned to SIEMENS AKTIENGESELLSCHAFT reassignment SIEMENS AKTIENGESELLSCHAFT ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: WAGNER, NORBERT
Publication of US20120275923A1 publication Critical patent/US20120275923A1/en
Abandoned legal-status Critical Current

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Classifications

    • 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
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F01D5/04—Blade-carrying members, e.g. rotors for radial-flow machines or engines
    • F01D5/043—Blade-carrying members, e.g. rotors for radial-flow machines or engines of the axial inlet- radial outlet, or vice versa, type
    • F01D5/048—Form or construction
    • 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
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/16—Arrangement of bearings; Supporting or mounting bearings in casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/04—Units comprising pumps and their driving means the pump being fluid-driven
    • 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
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—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
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/057—Bearings hydrostatic; hydrodynamic
    • 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

Definitions

  • the invention relates to a radial compressor having a rotor arrangement, which has a rotating shaft, a corotating rotor wheel arranged on the shaft, and a shaft bearing arranged on the shaft.
  • one or more rotor wheels rotates on a shaft as rotating wheels which perform fluid-dynamic work in order, for example, to compress a gaseous medium in a compressor or to drive a generator in a steam turbine.
  • the shaft is supported at at least two locations.
  • One example that may be mentioned is a radial compressor, in which the rotor wheels are arranged between the bearing locations and possibly also as an overhung stage at the free shaft end. Owing to a high overhang moment, there may be considerable vibration and, as a result, a maximum possible speed of rotation may be undesirably low.
  • the rotor is less sensitive to vibrational excitation and can therefore be moved at a high speed of rotation.
  • the invention can be employed to particular advantage if the rotor wheel is part of an overhung stage.
  • the absence of an obstruction in the region of the shaft axis makes it possible to achieve an enlarged intake cross section in comparison with radial induction of the air with a rotor wheel of the same diameter.
  • the shaft expediently ends in the rotor wheel, a free, i.e. unsupported, shaft end is necessarily formed. If the rotor wheel is arranged at the free shaft end, it is not possible for bending of the shaft to be counteracted there by a bearing, in particular a radial bearing. Consequently, moments which are critical in terms of bending and hence speeds of rotation which are critical in terms of bending can arise, imposing a disadvantageous restriction on the operating range of the turbomachine. By means of the invention, corresponding vibration can be reduced and the speed of rotation which can be achieved can be kept high.
  • the advantage of the embodiment according to the invention of the support for the shaft additionally lies in a reduction in the length of the shaft made possible by the design and, in particular, a reduction in the length of the free shaft end, thereby making it possible to achieve advantageous rotor dynamics
  • the recess is arranged on the wheel-disk side in the rotor wheel.
  • the wheel-disk side of a rotor wheel is the side facing away from the flow.
  • the rotor wheel has an oppositely situated shroud ring side which faces axially outward.
  • a seal can be arranged between the shaft bearing and the rotor wheel, advantageously being arranged in the recess, in particular completely within the recess.
  • the seal can be a labyrinth seal for sealing off bearing oil from the outside and/or for sealing off from the outside a working pressure built up within the compressor.
  • the size of the recess is advantageously dimensioned in such a way that a stator-side bearing receptacle of the shaft bearing projects into the recess. Stable support for the shaft close to the shaft end can thereby be achieved.
  • stator-side bearing receptacle also carries the seal in addition to the shaft bearing.
  • the invention is explained in greater detail with reference to an illustrative embodiment, which is shown in the drawing.
  • the single figure of the drawing shows a scrap view of a turbomachine 2 embodied as a radial compressor.
  • the illustration shows a schematic section along the shaft 4 of the turbomachine 2 .
  • the shaft 4 is part of a rotor 6 of the turbomachine 2 and, at one end, carries a rotor wheel 8 for inducing external air in the axial direction 10 and compressing the induced air in a radially outward direction.
  • the turbomachine 2 is a radial compressor having an overhung stage, i.e. a compressor stage with a rotor wheel 8 which is arranged at one axial end of the shaft 4 .
  • the radial compressor is of particularly large design and is used for air compression at volume flows of between 100,000 m 3 /h and 800,000 m 3 /h and compression from atmospheric pressure to between 4 bar and 8 bar.
  • the shaft 4 is supported by a first shaft bearing 12 embodied as a radial bearing and a second shaft bearing 14 embodied as an axial bearing.
  • the shaft 4 is supported by another radial shaft bearing, but this is arranged outside the area illustrated in the figure and is therefore not shown.
  • a shaft seal 16 in the form of a labyrinth seal is arranged between the radial shaft bearing 12 and the rotor wheel 8 in order to seal off the bearing oil from the outside.
  • the rotor wheel 8 ends radially toward the outside in blade segments 18 , which form a recess 20 toward the shaft 4 .
  • a boundary of this recess 20 on the wheel-disk side is represented by a dashed line 22 .
  • the radial shaft bearing 12 is arranged partially within this recess 20 , namely to an extent such that an axial center line 24 of the shaft bearing 12 is arranged in the recess 20 .
  • the axial center line 24 is formed by a section extending parallel to the shaft 4 in an imaginary axial central area of the shaft bearing 12 which intersects the shaft bearing 12 centrally in the axial direction 10 . More than half of a bearing area of the radial shaft bearing 12 is thus in the recess 20 of the rotor wheel 8 .
  • the shaft bearing 16 arranged around the shaft 4 is completely in the recess 20 .
  • the recess is arranged on the wheel-disk side of the rotor wheel 8 , i.e. on the side which faces away from the side from which the medium to be compressed, in this illustrative embodiment external air, is induced.
  • wheel-disk side accordingly means on the side of the hub and facing away from the axial side of the rotor wheel which guides the flow.
  • the shaft seal 16 and the radial shaft bearing 12 are fixed on the stator of the turbomachine 2 by a stator-side bearing receptacle 26 , thereby fixing the shaft 4 in the desired position thereof within the stator.
  • the bearing receptacle 26 projects by a certain amount into the recess 20 of the rotor wheel 8 and surrounds the outside of the shaft bearing 12 and the shaft seal 16 at least partially for the purpose of fixing.
  • the bearing receptacle 26 supports both the radial shaft bearing 12 and the shaft seal 16 by means of an element of integral design.
  • Arranging the radial bearing 12 at least partially within the recess 20 enables the shaft 4 to be designed with a shorter length than known shafts, thereby making it possible to achieve rotor dynamics which are favorable in respect of vibration.
  • the projecting part of the rotor wheel 8 the part extending in the circumferential direction and situated radially on the outside, which comprises the blade segments 18 , projects at least partially beyond the radial bearing 12 on the wheel-disk side, and therefore the fixing of the radial bearing 12 is passed out of the recess 20 in a direction facing laterally away from the rotor wheel 8 . Accordingly, the bearing receptacle 26 of the shaft bearing 12 projects into the recess 20 together with the shaft bearing 12 .
  • Arranging the shaft bearing partially in the recess 20 achieves a reduction in the length of the overhang and, as a result, a reduction in sensitivity to vibration.
  • rotor dynamics are thereby improved, with an increase in the speed of rotation critical in terms of bending at the free end, thus allowing the radial compressor to be operated at higher speeds of rotation as compared with conventional embodiments of overhung stages.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)
US13/509,122 2009-11-12 2010-11-10 Rotor for a turbo-machine Abandoned US20120275923A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102009052931.4 2009-11-12
DE102009052931A DE102009052931A1 (de) 2009-11-12 2009-11-12 Rotor für eine Strömungsmaschine
PCT/EP2010/067184 WO2011058042A2 (de) 2009-11-12 2010-11-10 Rotor für eine strömungsmaschine

Publications (1)

Publication Number Publication Date
US20120275923A1 true US20120275923A1 (en) 2012-11-01

Family

ID=43901925

Family Applications (1)

Application Number Title Priority Date Filing Date
US13/509,122 Abandoned US20120275923A1 (en) 2009-11-12 2010-11-10 Rotor for a turbo-machine

Country Status (5)

Country Link
US (1) US20120275923A1 (zh)
EP (1) EP2499339A2 (zh)
CN (1) CN102686831A (zh)
DE (1) DE102009052931A1 (zh)
WO (1) WO2011058042A2 (zh)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016199821A1 (ja) * 2015-06-11 2016-12-15 株式会社Ihi 回転機械

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3027070B1 (fr) * 2014-10-09 2019-08-02 Cryostar Sas Turbomachine tournant a des vitesses elevees

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2939626A (en) * 1957-12-27 1960-06-07 Laval Steam Turbine Co Turbo-compressor
US3102490A (en) * 1961-07-18 1963-09-03 Thompson Ramo Wooldridge Inc Turbo pumping apparatus
US3115841A (en) * 1961-11-16 1963-12-31 Thompson Ramo Wooldridge Inc Pump assembly
US3898015A (en) * 1973-07-05 1975-08-05 Thune Eureka As Submergible liquid pump
US4756664A (en) * 1985-10-03 1988-07-12 Sundstrand Corporation Scavenge oil system

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH201075A (de) * 1937-03-23 1938-11-15 Maschf Augsburg Nuernberg Ag Abgasturbogebläse.
DE966394C (de) * 1951-11-18 1957-08-01 Bayerische Motoren Werke Ag Abgasturbolader fuer Brennkraftmaschinen
US3219260A (en) * 1962-01-18 1965-11-23 Marion E Lamkin Propellant driven fan
US3692436A (en) * 1971-05-20 1972-09-19 Caterpillar Tractor Co Thermal compensating support for turbocharger shafts
JPH0681884B2 (ja) * 1988-07-25 1994-10-19 いすゞ自動車株式会社 翼車軸の軸受構造
US4878805A (en) * 1988-10-20 1989-11-07 Sundstrand Corporation Blower for use in particle contaminated environments
DE10003153A1 (de) * 2000-01-26 2001-08-02 Leybold Vakuum Gmbh Turboradialgebläse
US6430917B1 (en) * 2001-02-09 2002-08-13 The Regents Of The University Of California Single rotor turbine engine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2939626A (en) * 1957-12-27 1960-06-07 Laval Steam Turbine Co Turbo-compressor
US3102490A (en) * 1961-07-18 1963-09-03 Thompson Ramo Wooldridge Inc Turbo pumping apparatus
US3115841A (en) * 1961-11-16 1963-12-31 Thompson Ramo Wooldridge Inc Pump assembly
US3898015A (en) * 1973-07-05 1975-08-05 Thune Eureka As Submergible liquid pump
US4756664A (en) * 1985-10-03 1988-07-12 Sundstrand Corporation Scavenge oil system

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016199821A1 (ja) * 2015-06-11 2016-12-15 株式会社Ihi 回転機械
JP2017002822A (ja) * 2015-06-11 2017-01-05 株式会社Ihi 回転機械

Also Published As

Publication number Publication date
WO2011058042A3 (de) 2012-03-01
CN102686831A (zh) 2012-09-19
WO2011058042A2 (de) 2011-05-19
DE102009052931A1 (de) 2011-05-26
EP2499339A2 (de) 2012-09-19

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Legal Events

Date Code Title Description
AS Assignment

Owner name: SIEMENS AKTIENGESELLSCHAFT, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:WAGNER, NORBERT;REEL/FRAME:028189/0379

Effective date: 20120508

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION